JPWO2019146099A1 - Air conditioner - Google Patents

Abstract

The air conditioner according to the present invention includes a compressor, a condenser, an expansion valve, an evaporator, a receiver connected between the condenser and the expansion valve to store excess refrigerant, and the receiver and the expansion valve. An air conditioner having a pump connected between the two and performing a compression cycle and a pump cycle, the receiver comprising a first inlet, which is an inlet for flowing refrigerant into the receiver. The compressor is provided with a first outlet, which is an outlet for discharging the refrigerant from the condenser, at a position lower than the first inlet, and the refrigerant circulation circuit is a first end on the refrigerant inflow side. The end is connected between the first outlet and the first inlet at a position lower than the first inlet, and the second end, which is the end on the refrigerant outflow side, is the receiver and the pump. It is equipped with a bypass pipe connected between the two.

Description

The present invention relates to an air conditioner capable of performing both a compression cycle and a pump cycle.

Conventionally, it has a compressor, a condenser, an expansion valve, an evaporator, a receiver connected between the condenser and the expansion valve to store excess refrigerant, and a pump connected between the receiver and the expansion valve. An air conditioner including a refrigerant circulation circuit in which a refrigerant circulates inside is known (see Patent Document 1). Such an air conditioner can perform both compression and pump cycles. The compression cycle is an operation of driving the compressor, stopping the pump, and circulating the refrigerant in the refrigerant circulation circuit. Further, the pump cycle is an operation of driving the pump, stopping the compressor, and circulating the refrigerant in the refrigerant circulation circuit.

Japanese Unexamined Patent Publication No. 2014-163530

As mentioned above, conventional air conditioners capable of performing both compression and pump cycles include a receiver downstream of the condenser to store excess refrigerant. That is, the refrigerant flowing out of the condenser flows into the receiver and is temporarily stored, and the refrigerant flows out from the receiver as much as necessary. Here, in the condenser, the gaseous refrigerant is cooled, condensed and liquefied. Therefore, the liquid refrigerant flows out from the condenser. Therefore, the outlet of the refrigerant of the condenser is generally provided at the lower part of the condenser so that the liquid refrigerant can easily flow out from the condenser. Further, in the receiver, the outlet of the refrigerant is provided at, for example, the lower part of the receiver, and the inlet of the refrigerant is provided above the outlet of the receiver. Therefore, the outlet of the refrigerant of the condenser is lower than the inlet of the refrigerant of the receiver. Therefore, in order for the refrigerant flowing out of the condenser to flow into the receiver, the refrigerant flowing out from the refrigerant outlet of the condenser must rise and head toward the inlet of the receiver. That is, the pipe connecting the condenser and the receiver extends upward from the refrigerant outlet of the condenser and is connected to the refrigerant inlet of the receiver.

When switching the operating state of the air conditioner from the compression cycle to the pump cycle, the pump is started after the compressor is stopped. At this time, in order to start the pump, a liquid refrigerant must be supplied to the suction port of the pump. Therefore, in order to start the pump, after stopping the compressor, it is necessary to wait for the refrigerant to naturally convection in the refrigerant circulation circuit and for the liquid refrigerant to be supplied to the suction port of the pump. That is, in order to start the pump, the refrigerant liquefied by the condenser must reach the suction port of the pump through the receiver.

Here, in a conventional air conditioner capable of executing both a compression cycle and a pump cycle, in order for the refrigerant flowing out of the condenser to flow into the receiver, the refrigerant flowing out from the refrigerant outlet of the condenser must be used. It needs to rise and flow into the inlet of the receiver. Therefore, in order for the refrigerant flowing out of the condenser to flow into the receiver, it is necessary for the condenser to store a liquid refrigerant having a height equal to or higher than the height of the pipe connecting the condenser and the receiver. Therefore, in a conventional air conditioner capable of performing both a compression cycle and a pump cycle, when the operating state is changed from the compression cycle to the pump cycle, it takes time for the liquid refrigerant to be supplied to the suction port of the pump. There is a problem that it takes a long time to start the pump.

The present invention has been made to solve the above-mentioned problems, and can execute both a compression cycle and a pump cycle, and when the operating state is changed from the compression cycle to the pump cycle, until the pump is started. The purpose is to obtain an air conditioner that can shorten the time required for.

The air conditioner according to the present invention includes a compressor, a condenser, an expansion valve, an evaporator, a receiver connected between the condenser and the expansion valve to store excess refrigerant, and the receiver and the expansion valve. A compression cycle having a pump connected between the two, including a refrigerant circulation circuit in which a refrigerant circulates inside, driving the compressor, stopping the pump, and circulating the refrigerant in the refrigerant circulation circuit, and the above. An air conditioner that drives a pump, stops the compressor, and circulates the refrigerant in the refrigerant circulation circuit, and the receiver is an inflow port for flowing the refrigerant into the receiver. The condenser is provided with a first inflow port, the condenser is provided with a first outlet which is an outlet for discharging a refrigerant from the condenser at a position lower than the first inflow port, and the refrigerant circulation circuit is provided with a refrigerant inflow. The first end, which is a side end, is connected between the first outlet and the first inflow port at a position lower than the first inflow port, and is the second end, which is the end on the refrigerant outflow side. The unit includes a bypass pipe connected between the receiver and the pump.

The air conditioner according to the present invention can bypass the receiver and supply the liquid refrigerant flowing out of the condenser to the pump by a bypass pipe. Therefore, the air conditioner according to the present invention can shorten the time required to supply the liquid refrigerant to the suction port of the pump when the operating state is switched from the compression cycle to the pump cycle, and until the pump is started. Time can be shortened compared to the conventional method.

It is a refrigerant circuit diagram of the air conditioner which concerns on Embodiment 1 of this invention. It is a figure which observed the inside of the outdoor unit of the air conditioner which concerns on Embodiment 1 of this invention from the side. It is a figure which shows an example of the condenser of the air conditioner which concerns on Embodiment 1 of this invention. It is a figure which observed the inside of the outdoor unit of the air conditioner which concerns on Embodiment 2 of this invention from the side.

Embodiment 1.
FIG. 1 is a refrigerant circuit diagram of the air conditioner according to the first embodiment of the present invention.
The air conditioner 100 according to the first embodiment includes a refrigerant circulation circuit 101 in which a refrigerant circulates inside. Further, the refrigerant circulation circuit 101 includes a compressor 1, a condenser 10, an expansion valve 2, an evaporator 3, and a receiver 4 connected between the condenser 10 and the expansion valve 2 to store excess refrigerant. , A pump connected between the receiver 4 and the expansion valve 2.

Specifically, the inlet of the refrigerant of the condenser 10 is connected to the discharge port of the compressor 1 by piping. The condenser 10 according to the first embodiment includes a first condenser 11 and a second condenser 12. The first condenser 11 and the second condenser 12 are connected in parallel to the discharge port of the compressor 1. When the heat exchange load can be covered only by the first condenser 11, the condenser 10 may be composed of only the first condenser 11.

Further, the condenser 10 is also connected to the receiver 4 by piping. Specifically, the condenser 10 includes a first outlet 11a, which is an outlet for discharging the refrigerant from the condenser 10. Further, the receiver 4 includes a first inflow port 4a, which is an inflow port for flowing the refrigerant into the receiver 4. Then, the first outlet 11a of the condenser 10 and the first inlet 4a of the receiver 4 are connected by piping.

Here, as described above, the condenser 10 according to the first embodiment includes a first condenser 11 and a second condenser 12. Therefore, the first condenser 11 and the second condenser 12 are connected to the first inflow port 4a of the receiver 4 by piping as follows. The first condenser 11 includes a first outlet 11a. That is, the first outlet 11a is an outlet for flowing out the refrigerant that has flowed through the first condenser 11. Further, the second condenser 12 includes a second outlet 12a, which is an outlet for discharging the refrigerant from the second condenser. Then, the first outlet 11a of the first condenser 11 and the second outlet 12a of the second condenser 12 are connected by piping in parallel to the first inlet 4a of the receiver 4. That is, the first condenser 11 and the second condenser 12 are connected in parallel between the compressor 1 and the receiver 4.

More specifically, the refrigerant circulation circuit 101 includes a first pipe 22 and a second pipe 23. The first pipe 22 is a pipe that connects the second outlet 12a of the second condenser 12 and the first inlet 4a of the receiver 4. Further, the second pipe 23 is a pipe in which one end is connected to the first outlet 11a of the first condenser 11 and the other end is connected to the first pipe 22. The first outlet 11a of the first condenser 11 and the second outlet 12a of the second condenser 12 are parallel to the first inlet 4a of the receiver 4 by the first pipe 22 and the second pipe 23. It is connected.

The outlet of the refrigerant of the receiver 4 is connected to the suction port of the pump 5 by piping. Further, the discharge port of the pump 5 is connected to the inlet of the refrigerant of the expansion valve 2 by piping. The expansion valve 2 is, for example, a capillary tube or an electronic expansion valve. The outlet of the refrigerant of the expansion valve 2 is connected to the inlet of the refrigerant of the evaporator 3 by piping. The outlet of the refrigerant of the evaporator 3 is connected to the suction port of the compressor 1.

Further, the refrigerant circulation circuit 101 according to the first embodiment includes a bypass pipe 21. The first end 21a, which is the end of the bypass pipe 21 on the refrigerant inflow side, is connected between the first outlet 11a of the condenser 10 and the first inlet 4a of the receiver 4. Further, the second end portion 21b, which is the end portion of the bypass pipe 21 on the refrigerant outflow side, is connected between the receiver 4 and the pump 5. Since the refrigerant circulation circuit 101 has the bypass pipe 21, a part of the refrigerant flowing out from the condenser 10 can bypass the receiver 4 and flow to the suction port side of the pump 5.

As described above, the condenser 10 according to the first embodiment of the present character includes the first condenser 11 and the second condenser 12. The first outlet 11a is provided in the first condenser 11. Therefore, the first end portion 21a of the bypass pipe 21 is connected to the second pipe 23 that connects the first outlet 11a of the first condenser 11 and the first pipe 22. That is, all the refrigerant flowing out of the second condenser 12 flows to the pump 5 through the receiver 4. On the other hand, a part of the refrigerant flowing out from the first condenser 11 flows to the pump 5 through the receiver 4. Further, the remaining part of the refrigerant flowing out of the first condenser 11 bypasses the receiver 4 and flows to the pump 5.

Further, although the refrigerant circulation circuit 101 is not indispensable for the refrigerant circulation circuit 101, it includes a check valve 31, an expansion valve 34, an expansion valve 35, and a supercooling heat exchanger 6.

The check valve 31 is provided in the second pipe 23 that connects the first outlet 11a of the first condenser 11 and the first pipe 22. Specifically, the second pipe 23 is provided with a check valve 31 at the following positions. In the second pipe 23, the connection point between the second pipe 23 and the bypass pipe 21 is referred to as the first connection point 23a. Further, in the second pipe 23, the connection point between the second pipe 23 and the first pipe 22 is referred to as a second connection point 23b. In this case, the second pipe 23 is provided with a check valve 31 between the first connection portion 23a and the second connection portion 23b. The check valve 31 is a check valve that regulates the flow of the refrigerant from the second connection point 23b to the first connection point 23a. By providing the check valve 31, as will be described later, it is possible to prevent the liquid refrigerant from falling into the first condenser 11, and it is possible to improve the cooling capacity of the air conditioner 100. In addition, when the liquid refrigerant falls asleep, it means that the liquid refrigerant accumulates.

The expansion valve 34 is, for example, a capillary tube or an electronic expansion valve. The expansion valve 34 is provided in a pipe connecting the discharge port of the compressor 1 and the inflow port of the refrigerant of the first condenser 11. Specifically, the pipe connected to the discharge port of the compressor 1 is branched in two directions on the way. Then, one of the branched pipes is connected to the inlet of the refrigerant of the first condenser 11. Further, the other side of the branched pipe is connected to the inflow port of the refrigerant of the second condenser 12. The expansion valve 34 is provided in the branching pipe that is connected to the refrigerant inlet of the first condenser 11. By providing the expansion valve 34, the amount of the refrigerant flowing into the first condenser 11 can be adjusted. It is also possible to adjust the amount of refrigerant flowing into the first condenser 11 by adjusting the length and thickness of the pipe connecting the discharge port of the compressor 1 and the inlet of the refrigerant of the first condenser 11. It may be. However, by providing the expansion valve 34, it becomes easy to adjust the amount of the refrigerant flowing into the first condenser 11.

The expansion valve 35 is, for example, a capillary tube or an electronic expansion valve. The expansion valve 35 is provided in the bypass pipe 21. By providing the expansion valve 35, the amount of the refrigerant flowing through the bypass pipe 21 can be adjusted. It may be possible to adjust the amount of refrigerant flowing through the bypass pipe 21 depending on the length and thickness of the bypass pipe 21. However, by providing the expansion valve 35, it becomes easy to adjust the amount of the refrigerant flowing through the bypass pipe 21.

The supercooling heat exchanger 6 is provided between the receiver 4 and the pump 5. By providing the supercooling heat exchanger 6, the liquid refrigerant flowing out from the receiver 4 is further cooled by the supercooling heat exchanger 6, and the degree of supercooling of the liquid refrigerant is increased. As a result, the cooling capacity of the air conditioner 100 is improved. In the refrigerant circulation circuit 101 according to the first embodiment, the second end portion 21b of the bypass pipe 21 is connected between the receiver 4 and the supercooling heat exchanger 6. Therefore, the liquid refrigerant flowing out of the bypass pipe 21 is also cooled by the supercooling heat exchanger 6 to increase the degree of supercooling. Therefore, the cooling capacity of the air conditioner 100 is further improved.

The air conditioner 100 provided with the refrigerant circulation circuit 101 configured in this way is a composite cycle type air conditioner capable of executing both a compression cycle and a pump cycle. In other words, the air conditioner 100 can switch between the compression cycle and the pump cycle. The compression cycle is an operation of driving the compressor 1, stopping the pump 5, and circulating the refrigerant in the refrigerant circulation circuit 101. The pump cycle is an operation of driving the pump 5, stopping the compressor 1, and circulating the refrigerant in the refrigerant circulation circuit 101.

Specifically, in the compression cycle, the compressor 1 compresses the refrigerant, the condenser 10 condenses the refrigerant, the expansion valve 2 expands the refrigerant, and the evaporator 3 evaporates the refrigerant. At this time, the refrigerant circulation circuit 101 according to the first embodiment has the bypass pipe 25 and the check valve 33 so that the refrigerant circulating in the refrigerant circulation circuit 101 can flow around the stopped pump 5. I have.

One end of the bypass pipe 25 is connected between the outlet of the refrigerant of the supercooling heat exchanger 6 and the suction port of the pump 5. Further, the other end of the bypass pipe 25 is connected between the discharge port of the pump 5 and the inlet of the refrigerant of the expansion valve 2. The check valve 33 is provided in the bypass pipe 25. The check valve 33 is a check valve that regulates the flow of the refrigerant from the discharge port side of the pump 5 to the suction port side of the pump 5 in the bypass pipe 25. By providing the bypass pipe 25 and the check valve 33, the refrigerant flowing out of the supercooling heat exchanger 6 can flow around the stopped pump 5 during the compression cycle in which the pump 5 is stopped. Further, during the pump cycle in which the pump 5 is driven, the check valve 33 can prevent the refrigerant discharged from the pump 5 from flowing to the suction port side of the pump 5 through the bypass pipe 25. The configuration for bypassing the stopped pump 5 is not limited to the bypass pipe 25 and the check valve 33. As a configuration for bypassing the stopped pump 5, the configuration used in the conventional composite cycle type air conditioner may be appropriately adopted.

The pump cycle is executed when the temperature of the indoor air which is the heat exchange target of the evaporator 3 is higher than the temperature of the outdoor air which is the heat exchange target of the condenser 10. During the pump cycle, by driving the pump 5, heat is absorbed from the indoor air by the refrigerant flowing through the evaporator 3, and the absorbed heat is carried to the condenser 10 by the refrigerant and released to the outdoor air by the condenser 10. To. At this time, the refrigerant circulation circuit 101 according to the first embodiment has the bypass pipe 24 and the check valve 32 so that the refrigerant circulating in the refrigerant circulation circuit 101 can flow around the stopped compressor 1. It has.

One end of the bypass pipe 24 is connected between the outlet of the refrigerant of the evaporator 3 and the suction port of the compressor 1. Further, the other end of the bypass pipe 24 is connected between the discharge port of the compressor 1 and the refrigerant inlet of the condenser 10. The check valve 32 is provided in the bypass pipe 24. The check valve 32 is a check valve that regulates the flow of the refrigerant from the discharge port side of the compressor 1 to the suction port side of the compressor 1 in the bypass pipe 24. By providing the bypass pipe 24 and the check valve 32, the refrigerant flowing out of the evaporator 3 can flow around the stopped compressor 1 during the pump cycle in which the compressor 1 is stopped. Further, during the compression cycle in which the compressor 1 is driven, the check valve 32 can prevent the refrigerant discharged from the compressor 1 from flowing to the suction port side of the compressor 1 through the bypass pipe 24. The configuration for bypassing the stopped compressor 1 is not limited to the bypass pipe 24 and the check valve 32. As a configuration for bypassing the stopped compressor 1, the configuration used in the conventional composite cycle type air conditioner may be appropriately adopted.

Each configuration of the refrigerant circulation circuit 101 described above is housed in the outdoor unit 110 or the indoor unit 120. Specifically, the outdoor unit 110 includes a receiver 4, a pump 5, a supercooling heat exchanger 6, a first condenser 11, a second condenser 12, a bypass pipe 21, a first pipe 22, a second pipe 23, and a bypass pipe. 25, a check valve 31, a check valve 33, an expansion valve 34, and an expansion valve 35 are housed. The indoor unit 120 includes a compressor 1, an expansion valve 2, an evaporator 3, a bypass pipe 24, and a check valve 32. The outdoor unit 110 is installed outdoors, for example. Further, the indoor unit 120 is installed, for example, in a room which is a space to be cooled. Further, the outdoor unit 110 is installed at a position higher than, for example, the indoor unit 120.

Subsequently, the arrangement relationship of each configuration housed in the outdoor unit 110 will be described.

FIG. 2 is a side view of the inside of the outdoor unit of the air conditioner according to the first embodiment of the present invention. In FIG. 2, the pipe connecting the discharge port of the compressor 1 and the inflow port of the refrigerant of the condenser 10 is shown as the pipe 102. Further, in FIG. 2, the pipe connecting the discharge port of the pump 5 and the inflow port of the refrigerant of the expansion valve 2 is shown as the pipe 103.

The outdoor unit 110 includes, for example, a substantially rectangular parallelepiped housing 111. A suction port 112 is formed in the lower part of the housing 111. Further, an air outlet 113 is formed in the upper part of the housing 111. The housing 111 accommodates the blower 114 in the vicinity of the air outlet 113, such as a position facing the air outlet 113. That is, as the blower 114 rotates, outdoor air is sucked into the housing 111 from the suction port 112 at the bottom of the housing 111. Then, the outdoor air sucked into the housing 111 is blown out of the housing 111 from the air outlet 113 at the upper part of the housing 111.

The housing 111 also houses a first condenser 11, a second condenser 12, and a supercooled heat exchanger 6. The second condenser 12 is arranged above the first condenser 11 in the housing 111. The supercooling heat exchanger 6 is arranged below the first condenser 11 in the housing 111. The first condenser 11, the second condenser 12, and the supercooling heat exchanger 6 are installed so as to be inclined with respect to the vertical direction. By installing the first condenser 11, the second condenser 12, and the supercooling heat exchanger 6 at an angle in this way, the first condenser 11, the second condenser, and the second condenser are compared with the case where the first condenser 11, the second condenser 12, and the supercooling heat exchanger 6 are installed along the vertical direction. The heat transfer area of 12 and the supercooled heat exchanger 6 can be increased.

In the first embodiment, each of the first condenser 11, the second condenser 12, and the supercooling heat exchanger 6 is provided with a plurality of heat transfer fins and a plurality of heat transfer tubes through which the refrigerant flows. It is a heat fin tube type heat exchanger. The plurality of heat transfer fins are arranged at a predetermined interval. In the case of FIG. 2, the plurality of heat transfer fins of the first condenser 11, the second condenser 12, and the supercooled heat exchanger 6 are arranged in the direction orthogonal to the paper surface at a predetermined interval. The plurality of heat transfer tubes penetrate each of the plurality of heat transfer fins constituting the heat exchanger together with these heat transfer tubes. In the case of FIG. 2, each of the plurality of heat transfer tubes of the first condenser 11, the second condenser 12, and the supercooled heat exchanger 6 penetrates the plurality of heat transfer fins in the direction orthogonal to the paper surface. That is, in the case of FIG. 2, each of the plurality of heat transfer tubes of the first condenser 11, the second condenser 12, and the supercooled heat exchanger 6 are arranged so as to extend in the direction orthogonal to the paper surface.

Further, in the first embodiment, the plurality of heat transfer tubes of the first condenser 11 and the plurality of heat transfer tubes of the second condenser 12 penetrate a common heat transfer fin. In other words, the plurality of heat transfer fins of the first condenser 11 and the plurality of heat transfer fins of the second condenser 12 are integrated. By configuring the first condenser 11 and the second condenser 12 in this way, when the first condenser 11 and the second condenser 12 are installed in the housing 111, they can be treated as one heat exchanger. , The first condenser 11 and the second condenser 12 can be easily installed in the housing 111. Of course, the plurality of heat transfer fins of the first condenser 11 and the plurality of heat transfer fins of the second condenser 12 may be formed separately.

Further, in the first embodiment, the plurality of heat transfer tubes of the second condenser 12 and the plurality of heat transfer tubes of the supercooled heat exchanger 6 penetrate a common heat transfer fin. In other words, the plurality of heat transfer fins of the second condenser 12 and the plurality of heat transfer fins of the supercooled heat exchanger 6 are integrated. By configuring the second condenser 12 and the supercooled heat exchanger 6 in this way, when the second condenser 12 and the supercooled heat exchanger 6 are installed in the housing 111, they are treated as one heat exchanger. Can be done. That is, when the supercooling heat exchanger 6 is installed in the housing 111, the condenser 10 and the supercooling heat exchanger 6 can be treated as one heat exchanger. Therefore, the supercooling heat exchanger 6 can be easily installed in the housing 111. Of course, the plurality of heat transfer fins of the second condenser 12 and the plurality of heat transfer fins of the supercooled heat exchanger 6 may be formed separately.

A receiver 4 is also housed in the housing 111. At this time, the receiver 4, the condenser 10, and the bypass pipe 21 have the following positional relationship. The second outlet 12a of the second condenser 12 is arranged at a position higher than the first inlet 4a of the receiver 4. Therefore, the receiver 22 from the second outlet 12a of the second condenser 12 without raising the first pipe 22 connecting the second outlet 12a of the second condenser 12 and the first inlet 4a of the receiver 4. It can be installed toward the first inflow port 4a of 4. That is, the refrigerant flowing out from the second outflow port 12a of the second condenser 12 can flow toward the first inflow port 4a of the receiver 4 and flow into the receiver 4 without rising.

The first outlet 11a of the first condenser 11 is arranged at a position lower than the first inlet 4a of the receiver 4. Therefore, the second pipe 23 connecting the first outlet 11a of the first condenser 11 and the first pipe 22 rises from the first outlet 11a of the first condenser 11 toward the first pipe 22. It will be installed like this. Therefore, the refrigerant flowing out from the first outlet 11a of the first condenser 11 rises by the height h from the first outlet 11a of the first condenser 11 to the first pipe 22, and then flows, and then the first 1 It flows into the receiver 4 through the pipe 22.

The first end 21a of the bypass pipe 21 is connected to the second pipe 23 at a position lower than the first inflow port 4a of the receiver 4. Therefore, as compared with the case where the refrigerant flowing out from the first outlet 11a of the first condenser 11 flows into the receiver 4, the refrigerant flowing out from the first outlet 11a of the first condenser 11 flows into the bypass pipe 21. The rising height of the refrigerant is low. Here, in the first embodiment, the first end portion 21a of the bypass pipe 21 is connected to the second pipe 23 at a position equal to or lower than the height of the first outlet 11a of the first condenser 11. Therefore, the refrigerant flowing out from the first outlet 11a of the first condenser 11 can flow into the bypass pipe 21 without rising.

Subsequently, the operation of the air conditioner 100 according to the first embodiment will be described.

First, the operation of the air conditioner 100 during the compression cycle will be described.
As described above, during the compression cycle, the compressor 1 is driven and the pump 5 is stopped. When the compressor 1 is driven, the gaseous refrigerant on the suction port side of the compressor 1 is sucked into the compressor 1 and compressed. The gaseous refrigerant compressed by the compressor 1 flows into the first condenser 11 and the second condenser 12. The gaseous refrigerant that has flowed into the second condenser 12 is cooled by the outdoor air to be condensed into a liquid refrigerant, which flows out from the second outlet 12a. All of the liquid refrigerant flowing out from the second outlet 12a of the second condenser 12 flows into the receiver 4 through the first pipe 22.

The gaseous refrigerant that has flowed into the first condenser 11 is cooled by the outdoor air to condense into a liquid refrigerant, which flows out from the first outlet 11a. A part of the liquid refrigerant flowing out from the first outlet 11a of the first condenser 11 flows into the receiver 4 through the second pipe 23 and the first pipe 22. Further, the remaining part of the liquid refrigerant flowing out from the first outlet 11a of the first condenser 11 bypasses the receiver 4 by passing through the second pipe 23 and the bypass pipe 21, and the supercooling heat exchanger 6 Inflow to.

Here, in the conventional air conditioner not provided with the bypass pipe 21, all the liquid refrigerant flowing out from the first outlet 11a of the first condenser 11 flows into the receiver 4. At this time, in order for the liquid refrigerant flowing out of the first condenser 11 to flow into the receiver 4, as described above, the height h from the first outlet 11a of the first condenser 11 to the first pipe 22 Must rise and flow. Therefore, it is difficult for the liquid refrigerant to flow from the first condenser 11 to the receiver 4. Therefore, in the conventional air conditioner that does not have the bypass pipe 21, the liquid refrigerant falls into the first condenser 11.

On the other hand, in the air conditioner 100 according to the first embodiment, a part of the liquid refrigerant flowing out from the first outlet 11a of the first condenser 11 passes through the second pipe 23 and the bypass pipe 21. It bypasses the receiver 4 and flows into the supercooled heat exchanger 6. As described above, the first end portion 21a of the bypass pipe 21 is connected to the second pipe 23 at a position lower than the first inflow port 4a of the receiver 4. Therefore, the flow of the liquid refrigerant from the first condenser 11 to the bypass pipe 21 is easier to flow than the flow from the first condenser 11 to the receiver 4. Therefore, the air conditioner 100 according to the first embodiment can suppress the liquid refrigerant from falling into the first condenser 11 as compared with the conventional air conditioner not provided with the bypass pipe 21, and the first condenser 11 The amount of liquid refrigerant that falls asleep in the air can be reduced. Therefore, the air conditioner 100 according to the first embodiment can improve the cooling capacity as compared with the conventional air conditioner not provided with the bypass pipe 21.

In the first embodiment, the first end portion 21a of the bypass pipe 21 is connected to the second pipe 23 at a position equal to or lower than the height of the first outlet 11a of the first condenser 11. Therefore, the liquid refrigerant is more easily flowed from the first condenser 11 to the bypass pipe 21. Therefore, it is possible to further suppress the liquid refrigerant from falling into the first condenser 11, and further improve the cooling capacity of the air conditioner 100.

Further, the condenser 10 according to the first embodiment includes a first condenser 11 and a second condenser 12. The second condenser 12 is arranged above the first condenser 11, and the second outlet 12a of the second condenser 12 is located higher than the first inlet 4a of the receiver 4. Therefore, the liquid refrigerant easily flows from the second condenser 12 to the receiver 4, and it is possible to prevent the refrigerant from falling into the second condenser 12. Therefore, the cooling capacity of the air conditioner 100 can be further improved.

Further, the air conditioner 100 according to the first embodiment includes a check valve 31 in the second pipe 23. Therefore, the air conditioner 100 according to the first embodiment can further suppress the liquid refrigerant from falling into the first condenser 11, and can further improve the cooling capacity. Specifically, when the second pipe 23 is not provided with the check valve 31, the liquid refrigerant that is about to flow out from the first outlet 11a of the first condenser 11 is prevented from flowing out from the first outlet 11a. A pressure corresponding to the liquid head ρgh is applied in the direction of the liquid head, and it becomes difficult for the liquid head to flow out from the first outlet 11a. In addition, ρ is the density of the liquid refrigerant, and g is the gravitational acceleration. On the other hand, since the air conditioner 100 according to the first embodiment includes the check valve 31 in the second pipe 23, the liquid refrigerant to flow out from the first outlet 11a of the first condenser 11 is liquid. It is possible to prevent the pressure of the head ρgh from being applied. Therefore, by providing the check valve 31 in the second pipe 23, it is possible to further suppress the liquid refrigerant from falling into the first condenser 11, and it is possible to further improve the cooling capacity of the air conditioner 100.

As for the liquid refrigerant that has flowed into the receiver 4, the necessary amount flows out from the receiver 4, and the surplus is stored in the receiver 4. The liquid refrigerant flowing out of the receiver 4 joins the liquid refrigerant bypassing the receiver 4 through the bypass pipe 21, and then flows into the supercooling heat exchanger 6. The liquid refrigerant flowing into the supercooling heat exchanger 6 is cooled by the supercooling heat exchanger 6 to increase the degree of supercooling, and then flows out from the supercooling heat exchanger 6. The liquid refrigerant flowing out of the supercooling heat exchanger 6 passes through the bypass pipe 25 and the check valve 33, bypasses the stopped pump 5, and flows into the expansion valve 2. The liquid refrigerant flowing into the expansion valve 2 expands to become a gas-liquid two-phase refrigerant and flows into the evaporator 3. The gas-liquid two-phase refrigerant that has flowed into the evaporator 3 absorbs heat from the indoor air and evaporates to become a gaseous refrigerant. The gaseous refrigerant flows out of the evaporator 3 and then is sucked into the compressor 1 and compressed again.

Next, the operation of the air conditioner 100 during the pump cycle will be described.
As described above, the pump cycle is executed when the temperature of the indoor air which is the heat exchange target of the evaporator 3 is higher than the temperature of the outdoor air which is the heat exchange target of the condenser 10. During the pump cycle, the pump 5 is driven and the compressor 1 is stopped. The liquid refrigerant discharged from the pump 5 passes through the expansion valve 2 and flows into the evaporator 3. The liquid refrigerant flowing into the evaporator 3 absorbs heat from the indoor air and evaporates to become a gaseous refrigerant. This gaseous refrigerant bypasses the stopped compressor 1 through the bypass pipe 24 and the check valve 33, and flows into the first condenser 11 and the second condenser 12. The gaseous refrigerant that has flowed into the second condenser 12 is cooled by the outdoor air to be condensed into a liquid refrigerant, which flows out from the second outlet 12a. All of the liquid refrigerant flowing out from the second outlet 12a of the second condenser 12 flows into the receiver 4 through the first pipe 22.

The gaseous refrigerant that has flowed into the first condenser 11 is cooled by the outdoor air to condense into a liquid refrigerant, which flows out from the first outlet 11a. A part of the liquid refrigerant flowing out from the first outlet 11a of the first condenser 11 flows into the receiver 4 through the second pipe 23 and the first pipe 22. Further, the remaining part of the liquid refrigerant flowing out from the first outlet 11a of the first condenser 11 bypasses the receiver 4 by passing through the second pipe 23 and the bypass pipe 21, and the supercooling heat exchanger 6 Inflow to. As described above, a part of the liquid refrigerant flowing out from the first condenser 11 by the bypass pipe 21 bypasses the receiver 4, so that the first condenser is compared with the conventional air conditioner not provided with the bypass pipe 21. It is possible to prevent the liquid refrigerant from falling into the first condenser 11, and it is possible to reduce the amount of the liquid refrigerant that falls into the first condenser 11. Therefore, the air conditioner 100 according to the first embodiment can improve the cooling capacity as compared with the conventional air conditioner not provided with the bypass pipe 21.

In the first embodiment, the first end portion 21a of the bypass pipe 21 is connected to the second pipe 23 at a position equal to or lower than the height of the first outlet 11a of the first condenser 11. Therefore, as described above, it is possible to further suppress the liquid refrigerant from falling into the first condenser 11, and further improve the cooling capacity of the air conditioner 100.

Further, the condenser 10 according to the first embodiment includes a first condenser 11 and a second condenser 12. The second condenser 12 is arranged above the first condenser 11, and the second outlet 12a of the second condenser 12 is located higher than the first inlet 4a of the receiver 4. Therefore, as described above, it is possible to prevent the refrigerant from falling into the second condenser 12, and it is possible to further improve the cooling capacity of the air conditioner 100.

Further, the air conditioner 100 according to the first embodiment includes a check valve 31 in the second pipe 23. Therefore, as described above, in the air conditioner 100 according to the first embodiment, the pressure of the liquid head ρgh is applied to the liquid refrigerant that is about to flow out from the first outlet 11a of the first condenser 11. Can be prevented. Therefore, by providing the check valve 31 in the second pipe 23, it is possible to further suppress the liquid refrigerant from falling into the first condenser 11, and it is possible to further improve the cooling capacity of the air conditioner 100.

As for the liquid refrigerant that has flowed into the receiver 4, the necessary amount flows out from the receiver 4, and the surplus is stored in the receiver 4. The liquid refrigerant flowing out of the receiver 4 joins the liquid refrigerant bypassing the receiver 4 through the bypass pipe 21, and then flows into the supercooling heat exchanger 6. The liquid refrigerant flowing into the supercooling heat exchanger 6 is cooled by the supercooling heat exchanger 6 to increase the degree of supercooling, and then flows out from the supercooling heat exchanger 6. The liquid refrigerant flowing out of the supercooling heat exchanger 6 is sucked into the pump 5 and discharged again from the pump 5.

Next, the operation of switching from the compression cycle to the pump cycle in the air conditioner 100 will be described.
When the operating state of the air conditioner 100 is switched from the compression cycle to the pump cycle, the pump 5 is started after the compressor 1 is stopped. At this time, in order to start the pump 5, a liquid refrigerant must be supplied to the suction port of the pump 5.

When the compressor 1 is stopped, in the refrigerant circulation circuit 101, the refrigerant flows from the range where the pressure was high during the compression cycle to the range where the pressure was low during the compression cycle. The range of high pressure during the compression cycle is the range from the discharge port of the compressor 1 to the inlet of the refrigerant of the expansion valve 2. The range of low pressure during the compression cycle is the range from the outlet of the refrigerant of the expansion valve 2 to the suction port of the compressor 1. That is, when the compressor 1 is stopped, the liquid refrigerant existing on the suction port side of the pump 5 flows into the evaporator 3. Therefore, for a while after the compressor 1 is stopped, the liquid refrigerant is not supplied to the suction port of the pump 5, and the pump 5 cannot be started.

Therefore, after the compressor 1 is stopped, the refrigerant flows in the refrigerant circulation circuit 101 by natural convection until the pump 5 can be started. Specifically, the liquid refrigerant that has flowed into the evaporator 3 evaporates to become a gaseous refrigerant, and flows out of the evaporator 3. The gaseous refrigerant flowing out of the evaporator 3 passes through the bypass pipe 24 and the check valve 33, bypasses the stopped compressor 1, and flows into the first condenser 11 and the second condenser 12. The gaseous refrigerant flowing into the first condenser 11 and the second condenser 12 condenses into a liquid refrigerant. When the liquid refrigerant reaches the suction port of the pump 5, the pump 5 can be started.

Here, in the conventional air conditioner not provided with the bypass pipe 21, all the liquid refrigerant flowing out from the first outlet 11a of the first condenser 11 flows into the receiver 4. At this time, in order for the liquid refrigerant flowing out of the first condenser 11 to flow into the receiver 4, as described above, the height h from the first outlet 11a of the first condenser 11 to the first pipe 22 Must rise and flow. That is, in order for the liquid refrigerant flowing out of the first condenser 11 to flow into the receiver 4, it must rise to the position of the second connection portion 23b and flow. Then, in order for the liquid refrigerant flowing out of the first condenser 11 to rise to the position of the second connection point 23b by natural convection, the liquid refrigerant is placed in the first condenser 11 to a position higher than the second connection point 23b. It needs to be stored. Therefore, in the conventional air conditioner not provided with the bypass pipe 21, it takes time for the liquid refrigerant to be stored in the receiver 4. That is, in the conventional air conditioner that does not have the bypass pipe 21, it takes time for the liquid refrigerant to flow out from the receiver 4 and for the liquid refrigerant to reach the suction port of the pump 5. Therefore, in the conventional air conditioner not provided with the bypass pipe 21, when the compression cycle is switched to the pump cycle, the time until the pump 5 is started becomes long.

On the other hand, in the air conditioner 100 according to the first embodiment, the liquid refrigerant flowing out of the first condenser 11 can flow through the bypass pipe 21. That is, when the liquid refrigerant flows through the bypass pipe 21, the liquid refrigerant flowing out of the first condenser 11 can flow to the downstream side of the receiver 4 by bypassing the receiver 4. Therefore, in the air conditioner 100 according to the first embodiment, when the compression cycle is switched to the pump cycle, the time required to supply the liquid refrigerant to the suction port of the pump 5 can be shortened as compared with the conventional case, and the pump 5 can be used. The time until startup can be shortened compared to the past.

At the end of the first embodiment, an example of a condenser 10 suitable for the air conditioner 100 will be introduced. As described above, the cooling capacity of the air conditioner 100 can be improved by suppressing the liquid refrigerant from falling into the condenser 10. By configuring the condenser 10 as follows, it is possible to further suppress the liquid refrigerant from falling into the condenser 10, and it is possible to further improve the cooling capacity of the air conditioner 100.

FIG. 3 is a diagram showing an example of a condenser of the air conditioner according to the first embodiment of the present invention. Note that FIG. 3A is a side view of the condenser 10. FIG. 3B is an enlarged view of the Q portion of FIG. 3A.

The condenser 10 shown in FIG. 3 is a heat transfer fin tube type heat exchanger including a plurality of heat transfer fins 17 and a plurality of heat transfer tubes 13 through which a refrigerant flows. The plurality of heat transfer fins 17 are arranged at a predetermined interval. In the case of FIG. 3, the plurality of heat transfer fins 17 are arranged in the direction orthogonal to the paper surface at a predetermined interval. Further, each of the heat transfer fins 17 has a substantially rectangular shape that is long in the vertical direction, and has a first end portion 17a and a second end portion 17b in the lateral direction. The plurality of heat transfer tubes 13 penetrate each of the heat transfer fins 17. In the case of FIG. 3, each of the heat transfer tubes 13 penetrates each of the heat transfer fins 17 in the direction orthogonal to the paper surface. That is, in the case of FIG. 3, each of the heat transfer tubes 13 is arranged so as to extend in the direction orthogonal to the paper surface.

Further, each of the heat transfer tubes 13 is arranged as shown in FIG. 3 (b). That is, each of the heat transfer tubes 13 is arranged in a plurality of rows in the lateral direction, that is, in the lateral direction of the heat transfer fins 17. In the case of FIG. 3B, each of the heat transfer tubes 13 is laterally divided into four rows. Further, in each row, a plurality of heat transfer tubes 13 are arranged at a predetermined interval in the vertical direction.

Further, the condenser 10 includes a connecting pipe 14, a connecting pipe 15, and a connecting pipe 16 for connecting the two heat transfer tubes 13. The connection pipe 14 is, for example, a U-shaped pipe, which connects one end of the heat transfer pipes 13 in adjacent rows. In the case of FIG. 3, the connection pipe 14 is a pipe that connects the ends of the heat transfer tubes 13 in the adjacent rows on the back side of the paper surface. The connecting pipe 14 may be integrally formed with the heat transfer tube 13, or may be formed separately from the heat transfer tube 13. When the connecting pipe 14 is formed separately from the heat transfer pipe 13, the connecting pipe 14 and the heat transfer pipe 13 are connected by brazing or the like.

The connecting pipe 15 is, for example, a U-shaped pipe, which connects the other ends of the heat transfer pipes 13 in adjacent rows. In the case of FIG. 3, the connection pipe 15 is a pipe that connects the ends of the heat transfer tubes 13 in the adjacent rows on the front side of the paper surface. The connecting pipe 15 may be integrally formed with the heat transfer tube 13, or may be formed separately from the heat transfer tube 13. When the connecting pipe 15 is formed separately from the heat transfer pipe 13, the connecting pipe 15 and the heat transfer pipe 13 are connected by brazing or the like.

The connection pipe 16 is, for example, a U-shaped pipe, and is a pipe that connects the heat transfer pipe 13 in the row on the first end 17a side and the heat transfer pipe 13 in the row on the second end 17b side. The connecting pipe 16 may be integrally formed with the heat transfer tube 13, or may be formed separately from the heat transfer tube 13. When the connecting pipe 16 is formed separately from the heat transfer pipe 13, the connecting pipe 15 and the heat transfer pipe 13 are connected by brazing or the like.

In the condenser 10 configured in this way, a plurality of heat transfer tubes 13 are connected to the connection pipe 14, the connection pipe 15, and the connection pipe 16, so that the flow as shown by the black arrow in FIG. 3B is shown. Road 18 is formed.

Specifically, at least one of the heat transfer tubes 13 in the row closest to the first end 17a is connected to a branch header (not shown) of the condenser 10, and the refrigerant flows in from the branch header. One of such heat transfer tubes 13 is referred to as a heat transfer tube 131. Further, at least one of the heat transfer tubes 13 in the row closest to the second end 17b is connected to a merging header (not shown) of the condenser 10, and the refrigerant flows out to the merging header. One of such heat transfer tubes 13 is referred to as a heat transfer tube 13n. The outlet of the refrigerant of the condenser 10 shown in FIG. 3 is provided in a merging header (not shown).

The above-mentioned heat transfer tube 131 is a heat transfer tube 13 in a row on the second end 17b side of the heat transfer tube 131, and is connected to a heat transfer tube 13 arranged one step below the heat transfer tube 131 by a connecting pipe 14. It is connected. In FIG. 3B, the heat transfer tube 13 connected to the heat transfer tube 131 by the connection pipe 14 is shown as the heat transfer tube 132. The heat transfer tube 132 is connected to the heat transfer tube 13 in the row on the second end 17b side of the heat transfer tube 132 by a connecting pipe 15 and is arranged one step below the heat transfer tube 132. Has been done. In FIG. 3B, the heat transfer tube 13 connected to the heat transfer tube 132 by the connection pipe 15 is shown as the heat transfer tube 133.

The heat transfer tube 133 is connected to the heat transfer tube 13 in the row closest to the second end portion 17b and located one step below the heat transfer tube 133 by a connecting pipe 14. In FIG. 3B, the heat transfer tube 13 connected to the heat transfer tube 133 by the connection pipe 14 is shown as the heat transfer tube 134. The heat transfer tube 134 is connected to the heat transfer tube 13 in the row closest to the first end 17a and located below the heat transfer tube 134 by a connecting pipe 16. In FIG. 3B, the heat transfer tube 13 connected to the heat transfer tube 134 by the connection pipe 16 is shown as the heat transfer tube 135. In addition, three flow paths 18 are formed in the range of the condenser 10 shown in FIG. 3 (b). Therefore, the heat transfer tube 135 is a heat transfer tube 13 arranged three steps below the heat transfer tube 131.

The flow path 18 is formed by connecting the heat transfer pipe 13 from the heat transfer tube 131 to the heat transfer tube 13n with the connection pipe 14, the connection pipe 15, and the connection pipe 16 as described above. When the condenser 10 is installed so that the longitudinal direction of the heat transfer fins 17 is along the vertical direction, the flow path 18 is horizontal from the upstream side to the downstream side in the flow direction of the refrigerant flowing through the flow path 18. Or it is in a state of tilting downward. Therefore, in the condenser 10 shown in FIG. 3, there is no portion in the flow path 18 where the refrigerant rises and the refrigerant flows smoothly, and the refrigerant can flow smoothly through the flow path 18, so that the liquid refrigerant does not fall asleep inside. Can be suppressed.

Further, as shown in FIG. 3B, the angle between the connecting pipe 16 and the horizontal direction is α. The connection pipe 16 constitutes a portion of the flow path 18 that flows from the second end portion 17b to the first end portion 17a. Therefore, even when the condenser 10 is installed so that the longitudinal direction of the heat transfer fin 17 is inclined toward the second end 17b side with respect to the vertical direction, the angle between the longitudinal direction of the heat transfer fin 17 and the vertical direction is set. When is α or less, the flow path 18 is in a state of being inclined horizontally or downward from the upstream side to the downstream side in the flow direction of the refrigerant flowing through the flow path 18. Therefore, the condenser 10 shown in FIG. 3 rises in the flow path 18 even when the condenser 10 is installed so that the longitudinal direction of the heat transfer fin 17 is tilted toward the second end 17b with respect to the vertical direction. As a result, there is no place where the refrigerant flows, and the refrigerant can flow smoothly through the flow path 18, so that it is possible to further suppress the liquid refrigerant from falling inside.

Further, as shown in FIG. 3B, the angle between the connecting pipe 14 and the horizontal direction is β. Similarly, the angle between the connecting pipe 15 and the horizontal direction is β. These connecting pipes 14 and 15 form a portion of the flow path 18 that flows from the first end portion 17a to the second end portion 17b. Therefore, even when the condenser 10 is installed so that the longitudinal direction of the heat transfer fin 17 is inclined toward the first end portion 17a with respect to the vertical direction, the angle between the longitudinal direction of the heat transfer fin 17 and the vertical direction is set. When is β or less, the flow path 18 is in a state of being inclined horizontally or downward from the upstream side to the downstream side in the flow direction of the refrigerant flowing through the flow path 18. Therefore, the condenser 10 shown in FIG. 3 rises in the flow path 18 even when the condenser 10 is installed so that the longitudinal direction of the heat transfer fin 17 is inclined toward the first end portion 17a with respect to the vertical direction. As a result, there is no place where the refrigerant flows, and the refrigerant can flow smoothly through the flow path 18, so that it is possible to further suppress the liquid refrigerant from falling inside.

As described above, the air conditioner 100 according to the first embodiment includes a refrigerant circulation circuit 101 in which the refrigerant circulates inside. The refrigerant circulation circuit 101 includes a compressor 1, a condenser 10, an expansion valve 2, an evaporator 3, a receiver 4 connected between the condenser 10 and the expansion valve 2 to store excess refrigerant, and the receiver 4 and the expansion valve. It has a pump 5 connected to and from 2. The air conditioner 100 drives the compressor 1 and stops the pump 5 to circulate the refrigerant in the refrigerant circulation circuit 101, and drives the pump 5 and stops the compressor 1 in the refrigerant circulation circuit 101. Execute a pump cycle that circulates the refrigerant. The receiver 4 includes a first inflow port 4a, which is an inflow port for flowing a refrigerant into the receiver 4. The condenser 10 is provided with a first outlet 11a, which is an outlet for discharging the refrigerant from the condenser 10, at a position lower than the first inlet 4a of the receiver 4. The refrigerant circulation circuit 101 includes a bypass pipe 21. The first end portion 21a, which is the end portion of the bypass pipe 21 on the refrigerant inflow side, is located at a position lower than the first inflow port 4a of the receiver 4, the first outlet 11a of the condenser 10 and the first inflow port of the receiver 4. It is connected to 4a. The second end 21b, which is the end of the bypass pipe 21 on the refrigerant outflow side, is connected between the receiver 4 and the pump 5.

The air conditioner 100 according to the first embodiment can bypass the receiver 4 and supply the liquid refrigerant flowing out of the condenser 10 to the pump 5 by the bypass pipe 21. Therefore, the air conditioner 100 according to the first embodiment can shorten the time required to supply the liquid refrigerant to the suction port of the pump 5 when the operating state is switched from the compression cycle to the pump cycle. The time until the pump 5 starts can be shortened as compared with the conventional case.

In addition, the inventors used an actual machine provided with the refrigerant circulation circuit 101 according to the first embodiment, and changed from a compression cycle to a pump cycle depending on whether the bypass pipe 21 was provided or not. The time until the pump 5 was started after the switching was compared. In the actual machine used for comparison, when the bypass pipe 21 was provided, the time until the pump 5 was started after switching from the compression cycle to the pump cycle was shortened by 30 seconds as compared with the case where the bypass pipe 21 was not provided. ..

Further, since the air conditioner 100 according to the first embodiment includes the bypass pipe 21, the liquid refrigerant may fall into the condenser 10 during both the compression cycle and the pump cycle as described above. It can be suppressed more than before, and the cooling capacity can be improved more than before.

The inventors compared the cooling capacity between the case where the bypass pipe 21 was provided and the case where the bypass pipe 21 was not provided by using the actual machine provided with the refrigerant circulation circuit 101 according to the first embodiment. In the actual machine used for comparison, when the bypass pipe 21 was provided, the cooling capacity was improved by 2% at both the compression cycle and the pump cycle as compared with the case where the bypass pipe 21 was not provided.

Embodiment 2.
The refrigerant circulation circuit 101 shown in the first embodiment is an example. If the refrigerant circulation circuit 101 has the bypass pipe 21 described above, the configuration of the refrigerant circulation circuit 101 may be appropriately changed according to the cooling capacity and the like required for the air conditioner 100. In the second embodiment, one modification of the refrigerant circulation circuit 101 will be introduced. In the second embodiment, items not particularly described will be the same as those in the first embodiment, and the same functions and configurations as those in the first embodiment will be described using the same reference numerals.

FIG. 4 is a side view of the inside of the outdoor unit of the air conditioner according to the second embodiment of the present invention.
The air conditioner 100 according to the second embodiment includes two condensers 10 and two supercooled heat exchangers 6 in order to increase the heat exchange capacity of the condenser 10 and the supercooled heat exchanger 6. Specifically, the condenser 10, the supercooling heat exchanger 6, the receiver 4, and the bypass pipe 21 are combined into one set. In this case, the refrigerant circulation circuit 101 of the air conditioner 100 includes two sets of a condenser 10, a supercooling heat exchanger 6, a receiver 4, and a bypass pipe 21. Each set is connected in parallel between the discharge port of the compressor 1 and the suction port of the pump 5.

The condenser 10 according to the second embodiment includes a first condenser 11 and a second condenser 12. That is, the refrigerant circulation circuit 101 according to the second embodiment includes two first condensers 11 and two second condensers 12. The two first condensers 11 are connected in parallel to the discharge port of the compressor 1. The second condenser 12 is connected in parallel to the discharge port of the compressor 1.

The air conditioner 100 according to the second embodiment includes a bypass pipe 21 in each set. Therefore, in each set, the air conditioner 100 according to the second embodiment can bypass the receiver 4 and supply a part of the liquid refrigerant flowing out of the condenser 10 to the pump 5. Therefore, in the air conditioner 100 according to the second embodiment, as compared with the case where each set does not include the bypass pipe 21, until the pump 5 is started when the operating state is switched from the compression cycle to the pump cycle. Time can be shortened. Further, the air conditioner 100 according to the second embodiment can improve the cooling capacity at both the compression cycle and the pump cycle as compared with the case where each set does not include the bypass pipe 21.

1 Compressor, 2 Expansion valve, 3 Evaporator, 4 Receiver, 4a 1st inlet, 5 Pump, 6 Overcooling heat exchanger, 10 Condenser, 11 1st condenser, 11a 1st outlet, 12 2nd Condenser, 12a 2nd outlet, 13 (131 to 13n) heat transfer pipe, 14 connection pipe, 15 connection pipe, 16 connection pipe, 17 heat transfer fin, 17a 1st end, 17b 2nd end, 18 flow path , 21 Bypass piping, 21a 1st end, 21b 2nd end, 22 1st piping, 23 2nd piping, 23a 1st connection, 23b 2nd connection, 24 Bypass, 25 Bypass, 31 Non-return Valve, 32 check valve, 33 check valve, 34 expansion valve, 35 expansion valve, 100 air conditioner, 101 refrigerant circulation circuit, 102 piping, 103 piping, 110 outdoor unit, 111 housing, 112 suction port, 113 blow Outlet, 114 blower, 120 indoor unit.

The air conditioner according to the present invention includes a compressor, a condenser, an expansion valve, an evaporator, a receiver connected between the condenser and the expansion valve to store excess refrigerant, and the receiver and the expansion valve. A compression cycle having a pump connected between the two, including a refrigerant circulation circuit in which a refrigerant circulates inside, driving the compressor, stopping the pump, and circulating the refrigerant in the refrigerant circulation circuit, and the above. An air conditioner that drives a pump, stops the compressor, and circulates the refrigerant in the refrigerant circulation circuit, and the receiver is an inflow port for flowing the refrigerant into the receiver. The condenser is provided with a first inflow port, and the condenser is connected in parallel with the first condenser between the first condenser and the compressor and the receiver, and is arranged above the first condenser. comprising a second condenser, wherein the first condenser, a first outlet which is the outlet for discharging the refrigerant from the first condenser, provided at a position lower than the first inlet, the first The 2 condenser has a second outlet, which is an outlet for discharging the refrigerant from the second condenser, at a position higher than the first inlet of the receiver, and the refrigerant circulation circuit is on the refrigerant inflow side. is connected between the first end portion is an end portion and the front Symbol first outlet and the first inlet, a second end which is an end portion of the refrigerant outflow side between the pump and the receiver It has a bypass pipe to be connected.

Claims (9)

It has a compressor, a condenser, an expansion valve, an evaporator, a receiver connected between the condenser and the expansion valve to store excess refrigerant, and a pump connected between the receiver and the expansion valve. It is equipped with a refrigerant circulation circuit in which the refrigerant circulates inside.
A compression cycle that drives the compressor and stops the pump to circulate the refrigerant in the refrigerant circulation circuit, and a pump cycle that drives the pump and stops the compressor to circulate the refrigerant in the refrigerant circulation circuit. It is an air conditioner that executes
The receiver includes a first inflow port, which is an inflow port for flowing a refrigerant into the receiver.
The condenser is provided with a first outlet, which is an outlet for discharging the refrigerant from the condenser, at a position lower than the first inlet.
The refrigerant circulation circuit
The first end, which is the end on the refrigerant inflow side, is connected between the first outlet and the first inflow port at a position lower than the first inflow port, and is the end on the refrigerant outflow side. An air conditioner including a bypass pipe whose two ends are connected between the receiver and the pump. According to claim 1, the first end of the bypass pipe is connected between the first outlet and the first inlet at a position equal to or lower than the height of the first outlet of the condenser. The air conditioner described. The condenser
With the first condenser having the first outlet,
A second condenser connected in parallel with the first condenser between the compressor and the receiver and arranged above the first condenser,
With
According to claim 1 or 2, the second condenser is provided with a second outlet, which is an outlet for discharging a refrigerant from the second condenser, at a position higher than the first inlet of the receiver. The air conditioner described. The refrigerant circulation circuit
A first pipe connecting the second outlet of the second condenser and the first inlet of the receiver,
A second pipe having one end connected to the first outlet of the first condenser and the other end connected to the first pipe.
With
The first end of the bypass pipe is connected to the second pipe.
In the second pipe, when the connection point between the second pipe and the bypass pipe is the first connection point and the connection point between the second pipe and the first pipe is the second connection point,
3. The second pipe is provided with a check valve between the first connection point and the second connection point to regulate the flow of the refrigerant from the second connection point to the first connection point. The air conditioner described in. The air conditioner according to any one of claims 1 to 4, wherein the refrigerant circulation circuit includes a supercooling heat exchanger provided between the receiver and the pump. The air conditioner according to claim 5, wherein the second end of the bypass pipe is connected between the receiver and the supercooled heat exchanger. The air conditioner according to claim 5 or 6, wherein the supercooling heat exchanger is arranged below the condenser. The condenser and the supercooling heat exchanger have a plurality of heat transfer fins arranged at a predetermined interval, and a plurality of heat transfer tubes that penetrate the plurality of heat transfer fins and allow a refrigerant to flow inside. It is a fin tube type heat exchanger equipped with
The method according to any one of claims 5 to 7, wherein the plurality of heat transfer tubes of the condenser and the plurality of heat transfer tubes of the supercooled heat exchanger penetrate a common heat transfer fin. Air conditioner. Claims 1 to claim that the flow path through which the refrigerant formed in the condenser flows is horizontally or downwardly inclined from the upstream side to the downstream side in the flow direction of the refrigerant flowing through the flow path. 8. The air conditioner according to any one of 8.

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