JP6309739B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner that adjusts the amount of refrigerant flowing through a refrigerant circuit using a receiver that accumulates refrigerant.

  In an air conditioner, a compressor, a four-way valve, a condenser, a throttling device, and an evaporator are sequentially connected by a pipe to form a refrigerant circuit in which refrigerant circulates. In the air conditioner described in Patent Document 1, a receiver for storing refrigerant is provided between a condenser and an evaporator, and a high-pressure side throttle device and a low-pressure side throttle device are connected before and after the receiver. The opening area of each expansion device is controlled so that the state quantity of the refrigerant circulating in the refrigerant circuit becomes a target value.

  In the above air conditioner, the refrigerant condensed by the condenser is decompressed by the high pressure side expansion device and flows into the receiver. And the refrigerant | coolant discharged | emitted from the receiver is pressure-reduced with a low voltage | pressure side expansion apparatus, and is supplied to an evaporator. Excess refrigerant is stored in the receiver, and the state quantity of the refrigerant such as the degree of superheat is controlled.

Japanese Patent Laid-Open No. 10-89780

  In the above air conditioner, there is one receiver in the refrigerant circuit. The amount of refrigerant circulating in the refrigerant circuit is adjusted by accumulating the refrigerant in the receiver or removing the refrigerant from the receiver. The optimum amount of refrigerant when the air-conditioning operation is performed varies depending on operation conditions such as the operation mode, the outside air temperature, and the room temperature. However, when there is one receiver, the adjustment of the refrigerant amount is limited to the volume of the receiver and may not be adjusted to the optimum refrigerant amount.

  In view of the above, an object of the present invention is to provide an air conditioner that can adjust the amount of refrigerant circulating in the refrigerant circuit to an optimum amount of refrigerant according to the operating state of the air conditioning operation.

  The air conditioner of the present invention includes a refrigerant circuit in which a compressor, a condenser, a throttle unit, and an evaporator are connected by piping, and the throttle unit includes a plurality of receivers that store the refrigerant, and an amount of refrigerant that circulates through the refrigerant circuit. And a plurality of flow rate adjusting devices for adjusting the amount of refrigerant stored in each receiver in order to adjust the flow rate.

  When the flow rate adjusting device operates according to the operating condition, the amount of refrigerant accumulated in each receiver is adjusted. Thereby, the amount of refrigerant circulating through the refrigerant circuit changes, and the optimum amount of refrigerant according to the operating situation is obtained.

  A plurality of flow control devices are arranged in series in the refrigerant circuit, a receiver is connected between adjacent flow control devices, and the flow control device located downstream of the receiver in the flow direction of the refrigerant operates, thereby receiving the receiver. The amount of refrigerant that accumulates in the refrigerant changes.

  When the flow rate adjusting device operates so that the refrigerant circulating in the refrigerant circuit decreases, the refrigerant accumulates in the receiver positioned upstream of the flow rate adjusting device in the flow direction of the refrigerant. When the flow rate adjusting device operates so that more refrigerant circulates in the refrigerant circuit, the refrigerant accumulated in the receiver positioned upstream of the flow rate adjusting device is discharged. In the flow direction of the refrigerant, the refrigerant does not accumulate in the receiver located on the downstream side of the flow rate adjusting device. Thus, the refrigerant | coolant amount collected for every receiver can be adjusted by operating a some flow control apparatus.

  A control device for controlling the opening degree of the flow rate adjusting device is provided, and the control device controls the opening degree of at least one flow rate adjusting device and fully opens the other flow rate adjusting device. Depending on the degree of opening of the flow rate adjusting device, the amount of refrigerant passing through the flow rate adjusting device changes, and the amount of refrigerant accumulated in the receiver can be adjusted. By controlling the opening degree of one or a plurality of flow rate adjusting devices, the number of receivers in which the refrigerant accumulates changes, and the amount of refrigerant that accumulates in the receivers can be adjusted.

  The volume of each receiver is the same, but the volume of at least one receiver should be different. The amount of refrigerant that can be accumulated in all receivers can be adjusted by the combination of receivers that accumulate refrigerant, and the amount of refrigerant that circulates can be adjusted more appropriately according to the operating conditions.

  When the air conditioner is composed of an indoor unit having an indoor heat exchanger and an outdoor unit having an outdoor heat exchanger, the outdoor heat exchanger has a volume smaller than that of the outdoor heat exchanger. When the volume of the receiver near the heat exchanger is smaller than the volume of the receiver near the indoor heat exchanger, and the volume of the outdoor heat exchanger is smaller than the volume of the indoor heat exchanger, the volume of the receiver near the outdoor heat exchanger is It is made larger than the volume of the receiver close to the indoor heat exchanger. Thereby, it can prevent that the refrigerant | coolant amount which circulates through a refrigerant circuit increases too much.

  When the opening degree of the plurality of flow rate adjusting devices becomes equal to or larger than the predetermined opening degree, the control device decreases the rotational speed of the compressor. When the refrigerant circulating in the refrigerant circuit passes through the plurality of flow control devices, a pressure loss occurs in the refrigerant. Therefore, even if the flow rate adjusting device is opened to near full open, the amount of circulating refrigerant cannot be increased, resulting in insufficient refrigerant. Therefore, when the rotational speed of the compressor is lowered, the pressure loss is reduced as the optimum amount of refrigerant corresponding to the rotational speed decreases. This makes it possible to operate the flow rate adjusting device within a controllable range without opening the flow rate adjusting device to near full open, thereby eliminating the shortage of refrigerant.

  The control device lowers the rotational speed of the fan that blows air toward the condenser when the rotational speed of the compressor is lowered by setting the opening degree of the plurality of flow control devices to a predetermined opening degree or more. When the opening degree of the plurality of flow control devices is equal to or greater than the predetermined opening degree, the refrigerant shortage occurs as described above. By reducing the rotation speed of the condenser fan, the heat exchange capacity of the condenser is reduced, and the gas refrigerant passes through the flow rate adjusting device. Therefore, the refrigerant does not accumulate in the receiver, and the amount of refrigerant that circulates can be increased as compared with the case where only the rotation speed of the compressor is lowered.

  A cooling pipe that cools the receiver by diverting a low-temperature refrigerant from the refrigerant circuit and a heating pipe that warms the receiver by diverting a high-temperature refrigerant from the refrigerant circuit are provided. When the receiver is cooled by the low-temperature refrigerant, the refrigerant in the receiver is liquefied, so that the refrigerant easily flows into the receiver, and the refrigerant accumulates in the receiver. When the receiver is warmed by the high-temperature refrigerant, the refrigerant in the receiver evaporates, so that the refrigerant is easily discharged from the receiver, and the refrigerant in the receiver is reduced.

  The receiver is composed of a plurality of tanks. Since a small tank can be used, the tank can be arranged in a small gap, and the degree of freedom of arrangement of the receiver is increased.

  A control device for controlling the opening degree of the flow rate adjusting device is provided so that the refrigerant amount circulating in the refrigerant circuit becomes an optimum refrigerant amount according to the air conditioning operation, and the control device is a mathematical expression representing a change in the discharge temperature of the compressor. Is used to determine whether or not the refrigeration cycle is stable, and after the refrigeration cycle is stabilized, the opening degree of the flow control device is controlled.

  By using the above formula, it is possible to accurately determine the timing at which the refrigeration cycle is stabilized. After the refrigeration cycle is stabilized, the opening degree of the flow rate adjusting device is controlled, and the circulating refrigerant amount can be adjusted efficiently.

  According to the present invention, by accumulating refrigerant using a plurality of receivers, the amount of refrigerant circulating can be set to the optimum refrigerant amount according to the operation status, and air conditioning operation can be performed efficiently.

The figure which shows the refrigerant circuit of the air conditioner of the 1st Embodiment of this invention. The figure which shows the refrigerating cycle at the time of the air_conditionaing | cooling operation of 1st Embodiment. The figure which shows the inside of the outdoor unit in which a plurality of receivers are arranged Receiver layout in outdoor unit Air conditioner control block diagram The figure which shows the refrigerant circuit of the air conditioner of 3rd Embodiment. The figure which shows the refrigerating cycle at the time of the air_conditionaing | cooling operation of 3rd Embodiment. The figure which shows the refrigerating cycle at the time of the heating operation of 3rd Embodiment. The figure which shows the refrigerating cycle of 6th Embodiment. Control flow chart when the flow control device is near full open Control flow chart when the flow control device is near full open Control flowchart of prevention of dew condensation according to seventh embodiment The figure which shows the receiver by which the cooling tube and heating tube of 8th Embodiment were wound The figure which shows the refrigerating cycle of 8th Embodiment. The figure which shows the refrigerating cycle of 9th Embodiment The figure which shows the inside of the outdoor unit where a plurality of tanks are arranged Diagram showing receiver composed of multiple tanks The figure which shows the tank of other forms Flowchart of refrigeration cycle stability determination of tenth embodiment (A) is a figure which shows the time change of the discharge temperature for every rotation speed of a compressor, (b) is a figure which shows the saturation curve of the discharge temperature for every parameter, (c) is discharge temperature according to the rotation speed of a compressor. Showing that the saturation curve changes (D) is a figure which shows that the saturation curve of discharge temperature changes according to outside air temperature, (e) is a figure which shows the approximate expression of the time change of discharge temperature.

(First embodiment)
As shown in FIG. 1, the air conditioner of this embodiment includes a refrigerant circuit in which a compressor 1, a condenser 2, a throttle unit 3, and an evaporator 4 are connected by piping. The throttle unit 3 includes a plurality of receivers 5 that store refrigerant and a plurality of flow rate adjusting devices 6 that adjust the amount of refrigerant circulating in the refrigerant circuit.

  The receiver 5 has one entrance. A connecting pipe 8 branched from a connecting pipe 7 that connects the condenser 2 and the evaporator 4 in the refrigerant circuit is connected to the inlet / outlet of the receiver 5. The flow rate adjusting device 6 is an expansion valve and adjusts the flow rate and pressure of the refrigerant circulating in the refrigerant circuit.

  In the present embodiment, three receivers 5A, 5B, 5C and two flow rate adjusting devices 6A, 6B are alternately arranged along the flow direction of the refrigerant. The high pressure side flow rate adjustment device 6A and the low pressure side flow rate adjustment device 6B are arranged in series in the refrigerant circuit. The high pressure side flow rate adjustment device 6A is located upstream of the low pressure side flow rate adjustment device 6B in the refrigerant flow direction. The first receiver 5A is between the condenser 2 and the high pressure side flow rate adjustment device 6A, the second receiver 5B is between the high pressure side flow rate adjustment device 6A and the low pressure side flow rate adjustment device 6B, and the third receiver 5C is the low pressure side flow rate adjustment device. Each is connected between the device 6B and the evaporator 4.

  This air conditioner is a separate type composed of an indoor unit 10 and an outdoor unit 11. The air conditioner performs air conditioning operations such as cooling operation and heating operation. As shown in FIG. 2, a four-way valve 12 is provided in the refrigerant circuit. The indoor unit 10 is provided with an indoor heat exchanger 13, and the outdoor unit 11 includes a compressor 1, a four-way valve 12, an outdoor heat exchanger 14, two flow rate adjusting devices 6 a and 6 b, and three receivers 5 a, 5 b and 5 c. Is provided. The outdoor unit 11 is provided with an outdoor heat exchanger fan 15, and the indoor unit 10 is provided with an indoor heat exchanger fan 16. In the figure, 17 is a two-way valve used for charging refrigerant, 18 is a three-way valve, and 19 is a two-way valve for bypass piping.

  The refrigerant discharged from the compressor 1 returns to the compressor 1 through the condenser 2, the throttle unit 3, and the evaporator 4. In this way, a refrigeration cycle is formed in which the refrigerant circulates through the refrigerant circuit. In the air conditioner of FIG. 2, the flow direction of the refrigerant is switched by the four-way valve 12 according to the operation mode of the air conditioning operation.

  In the cooling mode or the defrosting mode, the indoor heat exchanger 13 becomes the evaporator 4 and the outdoor heat exchanger 14 becomes the condenser 2. The first flow rate adjusting device 6a is the high pressure side flow rate adjusting device 6A, and the second flow rate adjusting device 6b is the low pressure side flow rate adjusting device 6B. The receiver 5a corresponds to the receiver 5A, the receiver 5b corresponds to the receiver 5B, and the receiver 5c corresponds to the receiver 5C.

  In the heating mode, the flow direction of the refrigerant is reversed, the indoor heat exchanger 13 becomes the condenser 2, and the outdoor heat exchanger 14 becomes the evaporator 4. The second flow rate adjusting device 6b is the high pressure side flow rate adjusting device 6A, and the first flow rate adjusting device 6a is the low pressure side flow rate adjusting device 6B. The receiver 5c corresponds to the receiver 5A, the receiver 5b corresponds to the receiver 5B, and the receiver 5a corresponds to the receiver 5C.

  The receiver 5 is a cylindrical container, and the volume and shape of each receiver 5 are the same. An entrance / exit is formed on the bottom surface of the receiver 5, and the entrance / exit is directed downward. The receiver 5 is positioned above the connection pipe 7 that connects the outdoor heat exchanger 14 and the indoor heat exchanger 13 and the flow rate adjusting devices 6. The connecting pipe 8 has a smaller diameter than the connection pipe 7 and is provided so as to extend upward from the connection pipe 7. The upper part of the connecting pipe 8 is connected to the bottom surface of the receiver 5, and the lower part is connected to the connecting pipe 7. The connection pipe 8 and the connection pipe 7 are connected in an inverted T shape.

  The receiver 5 provided in the outdoor unit 11 is disposed in the vicinity of the outdoor heat exchanger 14. As shown in FIGS. 3 and 4, the outdoor heat exchanger 14 is arranged on the back side of the outdoor unit 11, and a refrigerant circuit pipe or valve including a connection pipe 7 is provided on one side of the outdoor heat exchanger 14 in the left-right direction. Such parts are arranged. A gap is formed between each part. Each receiver 5 is arranged on one side in the outdoor unit 11 and arranged in a gap between components. Since the receiver 5 is arrange | positioned at the back side of the outdoor unit 11, it is hard to receive the influence of a solar heat and the receiver 5 does not become high temperature easily.

  A pipe connecting the discharge side of the compressor 1 and the outdoor heat exchanger 14 passes through the back side of the outdoor unit 11 and has a larger diameter than other pipes. Each receiver 5 is attached to this large-diameter pipe. Each receiver 5 is arranged separately from other pipes other than the large-diameter pipe. Each receiver 5 does not come into contact with other pipes or parts.

  As a method of fixing the receiver 5, the receiver 5 is brazed to the pipe, or the receiver 5 is fixed to the pipe by a binding member such as a band. Each receiver 5 is fixed so as not to contact each other. Since the high-temperature and high-pressure gas refrigerant flows through this pipe in a stable state during the cooling mode, vibration of the pipe is small. By fixing the receiver 5 to this pipe, vibration of the receiver 5 can be suppressed, and noise when the refrigerant enters and exits the receiver 5 can be eliminated. Further, even if the receiver 5 or the pipe vibrates, each receiver 5 does not come into contact with other pipes or parts other than the large-diameter pipe, so that no noise is generated. Since the shape of the gap in the outdoor unit 11 is complicated, the shape of the receiver 5 may be changed according to the shape of the gap. However, the volume of the receiver 5 is not changed.

  As shown in FIG. 5, the air conditioner includes a control device 20 that controls the refrigeration cycle and performs an air conditioning operation. The air conditioner includes a condenser temperature sensor 21 that detects the temperature of the condenser 2, an evaporator temperature sensor 22 that detects the temperature of the evaporator 4, and a discharge temperature that detects the discharge temperature of the refrigerant discharged from the compressor 1. A sensor 23, a suction temperature sensor 24 for detecting the suction temperature of the refrigerant sucked into the compressor 1, a room temperature sensor 25, and an outside air temperature sensor 26 are provided. The control device 20 controls the refrigeration cycle by controlling the operations of the compressor 1, the fans 15, 16 and the flow rate adjusting device 6 based on the outputs of these temperature sensors according to the air conditioning operation desired by the user.

  The control device 20 includes an indoor control unit provided in the indoor unit 10 and an outdoor control unit provided in the outdoor unit 11. The indoor control unit and the outdoor control unit are connected so as to be communicable with each other, and both cooperate to control operations of the indoor unit 10 and the outdoor unit 11.

  The plurality of flow rate adjusting devices 6 provided in the refrigerant circuit are the same type of expansion valve. The opening of the expansion valve can be varied between 0 and 500 steps. The expansion valve has an opening area corresponding to the opening, and the amount of refrigerant passing therethrough can be varied. Therefore, the magnitude of the opening degree of each flow rate adjustment device 6 corresponds to the magnitude of the refrigerant amount passing through the flow rate adjustment device 6. As the opening degree increases, the amount of refrigerant passing therethrough increases.

  By changing the opening degree of the high pressure side flow rate adjustment device 6A and the low pressure side flow rate adjustment device 6B, the amount of refrigerant passing through each flow rate adjustment device 6A, 6B changes, and the upstream side of each flow rate adjustment device 6A, 6B. A refrigerant pressure difference occurs between the downstream side and the downstream side. When the opening degree of the low pressure side flow rate adjustment device 6B is made larger than the opening degree of the high pressure side flow rate adjustment device 6A, the pressure on the upstream side of the high pressure side flow rate adjustment device 6A becomes higher than the pressure on the downstream side. The liquid refrigerant flows into the connecting pipe 8 of the first receiver 5A on the upstream side of the high-pressure side flow rate adjusting device 6A, and the liquid refrigerant accumulates in the first receiver 5A. Liquid refrigerant does not accumulate in the second receiver 5B and the third receiver 5C on the downstream side of the high-pressure side flow control device 6A. In addition, when the pressure in the 2nd receiver 5B is lower than the pressure of the refrigerant | coolant between the high pressure side flow volume adjustment apparatus 6A and the low pressure side flow volume adjustment apparatus 6B, a liquid refrigerant flows into the 2nd receiver 5B according to the pressure difference. Accumulate.

  Here, when the opening degree of the high pressure side flow rate adjusting device 6A is increased, the pressure on the upstream side of the high pressure side flow rate adjusting device 6A becomes lower. The liquid refrigerant accumulated in the first receiver 5A is discharged to the refrigerant circuit.

  When the opening degree of the high pressure side flow rate adjustment device 6A is made larger than the opening degree of the low pressure side flow rate adjustment device 6B, the pressure on the upstream side of the low pressure side flow rate adjustment device 6B becomes higher than the pressure on the downstream side. As a result, liquid refrigerant accumulates in the first receiver 5A and the second receiver 5B on the upstream side of the low-pressure flow rate adjustment device 6B, and the liquid refrigerant is stored in the third receiver 5C on the downstream side of the low-pressure flow rate adjustment device 6B. I do not collect.

  Here, when the opening degree of the low pressure side flow rate adjusting device 6B is increased, the pressure on the upstream side of the low pressure side flow rate adjusting device 6B becomes low. The liquid refrigerant accumulated in the first receiver 5A and the second receiver 5B is discharged to the refrigerant circuit.

  When the air conditioning operation is performed, the control device 20 controls the refrigeration cycle so that the room temperature becomes the set temperature. At this time, the control device 20 adjusts the amount of refrigerant so that the amount of refrigerant circulating through the refrigerant circuit is optimized in accordance with the operating conditions. A part of the refrigerant filled in the refrigerant circuit is accumulated in the receiver 5, and the remaining refrigerant circulates in the refrigerant circuit. Of the circulating refrigerant amount, the refrigerant amount when the COP is maximum is set as the optimum refrigerant amount. The optimum amount of refrigerant varies depending on the operation mode, and also varies depending on the rotation speed of the compressor 1, the outside air temperature, the room temperature, and the volume of the heat exchanger indoors and outdoors. For example, in the cooling mode, more refrigerant is required in the rapid cooling mode in which cooling is performed rapidly.

  When the air-conditioning operation is started, the control device 20 sets the target rotational speed of the compressor 1 based on the set temperature and the room temperature, and the high-pressure side and low-pressure side flow control devices 6A and 6B according to the target rotational speed. Determine the opening. The control device 20 controls the compressor 1, the flow rate adjusting devices 6A and 6B, the fans 15 and 16, and the like according to the determined operating conditions. Moreover, the control apparatus 20 determines the initial opening degree of each flow volume adjustment apparatus 6A, 6B according to target rotation speed and operation modes (cooling mode, heating mode, etc.).

  When the air conditioner is stopped, the high-pressure side and low-pressure side flow control devices 6A and 6B are fully opened. When the air conditioning operation is started, the control device 20 initializes the flow rate adjusting devices 6A and 6B. That is, after each flow rate adjusting device 6A, 6B is fully closed, each flow rate adjusting device 6A, 6B is opened to the initial opening degree. Thereafter, the compressor 1 is started and the refrigerant circulates through the refrigerant circuit.

  Here, at the time of starting the air conditioning operation, the control device 20 operates the flow rate adjusting devices 6A and 6B so that the opening degree of the low pressure side flow rate adjusting device 6B is larger than the opening degree of the high pressure side flow rate adjusting device 6A. . For example, the low pressure side flow rate adjustment device 6B is fully opened, and the high pressure side flow rate adjustment device 6A is set to the determined initial opening. During this time, the rotational speed of the compressor 1 is constant. The liquid refrigerant that has accumulated in the second receiver 5B flows out into the refrigerant circuit. Further, by opening the high-pressure flow rate adjusting device 6A, a part of the liquid refrigerant that has accumulated in the first receiver 5A on the upstream side flows out to the refrigerant circuit. As described above, when the refrigerant circulating in the refrigerant circuit is increased, the supercooling on the outlet side of the condenser 2 is increased, and the air conditioning capability can be enhanced. In the heating mode, warm air having a higher temperature can be blown out from the start of operation.

  When the refrigeration cycle is stabilized after the start of the air conditioning operation, the control device 20 performs refrigerant amount adjustment control so that the circulating refrigerant amount becomes the optimum refrigerant amount. The determination of the stability of the refrigeration cycle is made based on the temperature of the refrigerant discharged from the compressor 1. The control device 20 monitors the change in the discharge temperature based on the output of the discharge temperature sensor 23. When the change in the discharge temperature becomes small, the control device 20 recognizes that the discharge temperature is stable and determines that the refrigeration cycle is stable.

  In the refrigerant amount adjustment control, the opening degrees of the high-pressure side and low-pressure side flow rate adjusting devices 6A and 6B are set according to the operation state such as the operation mode, the degree of superheat, the rotational speed of the compressor 1, the outside air temperature, and the room temperature. When the refrigerant amount adjustment control is performed, the control device 20 determines the number of rotations of the compressor 1 based on the operation mode and the outside air temperature, sets an optimum amount of refrigerant according to the number of revolutions, and becomes the optimum amount of refrigerant. In this way, the opening degree of each flow rate adjusting device 6A, 6B is determined. And the control apparatus 20 controls each flow volume adjustment apparatus 6A, 6B so that it may become the determined opening degree. Note that the opening degree of each of the flow rate adjusting devices 6A and 6B according to the operating condition is determined in advance by experiments or the like and stored in the memory of the control device 20. During the air conditioning operation, the control device 20 reads the opening amounts of the flow rate adjustment devices 6A and 6B according to the current operation state from the memory, and operates the flow rate adjustment devices 6A and 6B according to the read opening amounts.

  When confirming that the refrigeration cycle is stable, the control device 20 operates the high-pressure side and low-pressure side flow rate adjustment devices 6A and 6B so that the set opening degree is obtained. That is, one flow rate adjusting device 6 is controlled and the other flow rate adjusting device 6 is fully opened. As the order of operation of the flow rate adjusting devices 6A and 6B, first, the other flow rate adjusting device 6 is fully opened, and then one flow rate adjusting device 6 operates to the set opening degree.

  When the opening of the high-pressure flow rate adjusting device 6A is controlled to the set opening, and the low-pressure flow rate adjusting device 6B is fully opened, the liquid refrigerant flows in and accumulates in the first receiver 5A. Liquid refrigerant does not accumulate in the second and third receivers 5B and 5C. That is, in the second and third receivers 5B and 5C, the liquid refrigerant that does not enter or exit or that has accumulated is discharged.

  In addition, when the opening of the low-pressure flow rate adjusting device 6B is controlled to the set opening and the high-pressure flow adjusting device 6A is fully opened, liquid refrigerant flows into the first and second receivers 5A and 5B. Accumulate. Liquid refrigerant does not accumulate in the third receiver 5C. That is, in the third receiver 5C, the refrigerant does not enter or exit or the liquid refrigerant that has accumulated is discharged. In this way, by controlling the flow rate adjustment device 6 located downstream of the receiver 5 in the refrigerant flow direction, the amount of refrigerant accumulated in the receiver 5 located upstream of the flow rate adjustment device 6 can be adjusted. it can.

  Moreover, you may control the opening degree of the two flow volume adjustment apparatuses 6. FIG. When the opening degree of the low pressure side flow rate adjusting device 6B is controlled to be larger than the opening degree of the high pressure side flow rate adjusting device 6A, a pressure difference occurs between the refrigerant flowing on the upstream side and the downstream side of each flow rate adjusting device 6. . While the liquid refrigerant accumulates in the first receiver 5A, a little liquid refrigerant accumulates also in the second receiver 5B. When the opening of the high pressure side flow control device 6A is controlled to be larger than the opening of the low pressure flow control device 6B, liquid refrigerant accumulates in the second receiver 5B and a little liquid refrigerant also in the first receiver 5A. Accumulate.

  Therefore, by controlling each flow rate adjusting device 6, the amount of refrigerant accumulated in each receiver 5 is different, and the amount of refrigerant circulating in the refrigerant circuit can be adjusted. And it can be made easy to the optimal refrigerant | coolant amount according to a driving | running condition. As a result, the air conditioner can be operated efficiently, and power consumption can be reduced and operating capacity can be improved.

  Here, since the operation state changes, the control device 20 changes the rotation speed of the compressor 1 according to the room temperature, the outside air temperature, and the like. The optimal amount of refrigerant changes as the rotational speed of the compressor 1 changes. When the rotation speed of the compressor 1 increases, the optimum refrigerant amount increases, and when the rotation speed of the compressor 1 decreases, the optimum refrigerant amount decreases.

  When increasing the amount of refrigerant circulating through the refrigerant circuit, the control device 20 fully opens the low-pressure side flow rate adjustment device 6B and controls the high-pressure side flow rate adjustment device 6A. In the first receiver 5A, liquid refrigerant flows in and accumulates, but in the second and third receivers 5B and 5C, the accumulated liquid refrigerant flows out. Accordingly, only the refrigerant amount corresponding to the volume of the first receiver 5A is accumulated, and the circulating refrigerant amount is increased.

  When reducing the amount of refrigerant circulating in the refrigerant circuit, the control device 20 fully opens the high-pressure side flow rate adjustment device 6A and controls the low-pressure side flow rate adjustment device 6B. In the first and second receivers 5A and 5B, liquid refrigerant flows in and accumulates, but in the third receiver 5C, the accumulated liquid refrigerant flows out. Therefore, the refrigerant accumulates according to the total volume of the first receiver 5A and the second receiver 5B, and the amount of refrigerant circulating is reduced.

  Further, when the outside air temperature or room temperature changes, the degree of superheat changes. The control device 20 controls the opening degree of each flow rate adjusting device 6 according to the change in the degree of superheat. The control device 20 determines a change in the degree of superheat based on the temperature of the evaporator 4 detected by the evaporator temperature sensor 22 or the suction temperature sensor 24. Further, the degree of superheat may be obtained based on the temperature on the inlet side of the evaporator 4 and the temperature on the suction side of the compressor 1.

  When the degree of superheat increases, the control device 20 performs control so that the opening degree of one flow rate adjustment device 6 is increased. For example, when the high pressure side flow rate adjustment device 6A is controlled, the liquid refrigerant accumulated in the first receiver 5A decreases when the opening of the high pressure side flow rate adjustment device 6A increases. As the refrigerant passing through the evaporator 4 increases, the degree of superheat decreases. Further, when the degree of superheat becomes small, the control device 20 performs control so that the opening degree of one flow rate adjustment device 6 becomes small. For example, when the high-pressure flow rate adjustment device 6A is controlled, the liquid refrigerant that accumulates in the first receiver 5A increases as the opening of the high-pressure flow rate adjustment device 6A decreases. As the refrigerant passing through the evaporator 4 decreases, the degree of superheat increases.

  In the above refrigerant circuit, the three receivers 5 and the two flow rate adjusting devices 6 are provided, but the number of receivers 5 may be two or four or more. Two or three flow rate adjusting devices 6 are provided for the two receivers 5. Three to five flow rate adjusting devices 6 are provided for the four receivers 5. Further, three or four flow rate adjusting devices 6 may be provided for the three receivers 5. The receiver 5 and the flow rate adjusting device 6 are alternately arranged in the flow direction of the refrigerant. The amount of refrigerant that can be controlled can be increased or decreased by the number of receivers 5 and the number of flow control devices 6. The larger the number, the more various refrigerant amounts can be adjusted.

(Second Embodiment)
In the air conditioner of the first embodiment, the indoor heat exchanger 13 installed in the indoor unit 10 and the outdoor heat exchanger 14 installed in the outdoor unit 11 may have different volumes. Due to the different volumes, the optimum refrigerant amount varies depending on the operation mode. When the volume of the outdoor heat exchanger 14 is larger than the volume of the indoor heat exchanger 13, the optimum refrigerant amount in the cooling mode is larger than the optimum refrigerant amount in the heating mode. When the volume of the indoor heat exchanger 13 is larger than the volume of the outdoor heat exchanger 14, the optimum refrigerant amount in the heating mode is larger than the optimum refrigerant amount in the cooling mode.

  Information on the size of the indoor and outdoor heat exchangers 13 and 14 is set in advance at the time of factory shipment or installation of the air conditioner. Based on this information, the control device 20 determines whether to increase or decrease the amount of refrigerant circulating during the air conditioning operation. And the control apparatus 20 controls the flow volume adjustment apparatus 6 so that it may become the optimal refrigerant | coolant amount according to an operation mode. The other configurations and operations except for the indoor and outdoor heat exchangers 13 and 14 are the same as those in the first embodiment.

  That is, when the volume of the condenser 2 is larger than the volume of the evaporator 4, the control device 20 controls the high pressure side flow rate adjustment device 6A and fully opens the low pressure side flow rate adjustment device 6B. The refrigerant accumulates in the first receiver 5A, and no refrigerant accumulates in the second and third receivers 5B and 5C. Thereby, the amount of circulating refrigerant can be increased. Conversely, when the control device 20 controls the low pressure side flow rate adjustment device 6B and fully opens the high pressure side flow rate adjustment device 6A, the refrigerant accumulates in the first and second receivers 5A and 5B, and the third receiver 5C receives the refrigerant. Will not accumulate. At this time, the amount of circulating refrigerant decreases.

  Here, in the cooling mode, the outdoor heat exchanger 14 becomes the condenser 2 and the indoor heat exchanger 13 becomes the evaporator 4. In the heating mode, the indoor heat exchanger 13 becomes the condenser 2 and the outdoor heat exchanger 14 becomes the evaporator 4. In any operation mode, the flow rate adjusting device 6 on the side close to the condenser 2 is controlled, and the flow rate adjusting device 6 on the side close to the evaporator 4 is fully opened, so that the amount of the circulating refrigerant increases.

  Therefore, when there is a difference in the volume of the heat exchangers 13 and 14 indoors and outdoors, the high pressure side flow rate adjustment device 6A is controlled and the low pressure side flow rate adjustment device 6B is fully opened. An amount of refrigerant can be circulated, and efficient air-conditioning operation can be performed. On the other hand, the flow of the refrigerant circulating in the refrigerant circuit is reversed between the cooling mode and the heating mode. For example, in the refrigerant circuit shown in FIG. 2, if the high-pressure flow rate adjustment device 6a is controlled and the low-pressure flow rate adjustment device 6b is fully opened, the liquid refrigerant accumulates in the receiver 5a during the cooling mode. Liquid refrigerant accumulates in 5c. At this time, when the volume of the indoor heat exchanger 13 is smaller than the volume of the outdoor heat exchanger 14, the volume of the receiver 5a is preferably smaller than the volume of the receiver 5c. When the volume of the outdoor heat exchanger 14 is smaller than the volume of the indoor heat exchanger 13, the volume of the receiver 5c is preferably smaller than the volume of the receiver 5a. By doing so, it is easy to avoid an excessive refrigerant state, and it is easy to operate with an optimal amount of refrigerant.

  In the air conditioner shown in FIG. 2, when the volume of the outdoor heat exchanger 14 is larger than the volume of the indoor heat exchanger 13, in the cooling mode, the control device 20 controls the first flow rate adjusting device 6a, 2 Fully open the flow rate adjusting device 6b. Liquid refrigerant accumulates only in the first receiver 5a, and the amount of refrigerant circulating in the refrigerant circuit increases. In the heating mode, the control device 20 controls the first flow rate adjusting device 6a and fully opens the second flow rate adjusting device 6b. Liquid refrigerant accumulates in the second and third receivers 5b and 5c, and the amount of refrigerant circulating in the refrigerant circuit decreases. The amount of refrigerant circulating in the cooling mode is larger than the amount of refrigerant circulating in the heating mode.

  When the volume of the indoor heat exchanger 13 is larger than the volume of the outdoor heat exchanger 14, in the cooling mode, the control device 20 controls the second flow rate adjustment device 6b to fully open the first flow rate adjustment device 6a. . Liquid refrigerant accumulates in the first and second receivers 5a and 5b, and the amount of refrigerant circulating in the refrigerant circuit decreases. In the heating mode, the control device 20 controls the second flow rate adjusting device 6b to fully open the first flow rate adjusting device 6a. Liquid refrigerant accumulates only in the third receiver 5c, and the amount of refrigerant circulating in the refrigerant circuit increases. The amount of refrigerant circulating in the heating mode is larger than the amount of refrigerant circulating in the cooling mode.

(Third embodiment)
In the air conditioner of the present embodiment, as shown in FIG. 6, the receivers are first and second receivers 5A and 5B, the high-pressure flow rate adjustment device 6A is disposed upstream of the first receiver 5A, and the second A low pressure side flow rate adjusting device 6B is arranged upstream of the receiver 5B. The low pressure side flow rate adjusting device 6B is located between the first receiver 5A and the second receiver 5B. Other configurations and operations excluding the receiver 5 are the same as those in the first embodiment.

  When the control device 20 controls the high pressure side flow rate adjustment device 6A and fully opens the low pressure side flow rate adjustment device 6B, the refrigerant does not enter and exit the first and second receivers 5A and 5B. When the control device 20 controls the low pressure side flow rate adjustment device 6B and fully opens the high pressure side flow rate adjustment device 6A, the liquid refrigerant accumulates in the first receiver 5A.

  As described above, when the flow rate adjusting device 6 positioned on the downstream side of the receiver 5 is operated, the liquid refrigerant is accumulated in the receiver 5 positioned on the upstream side of the flow rate adjusting device 6. That is, the amount of refrigerant that accumulates in the receiver 5 when the downstream flow rate adjustment device 6 operates is greater than the amount of refrigerant that accumulates in the receiver 5 when the upstream flow rate adjustment device 6 operates. Therefore, the amount of refrigerant that circulates when the high-pressure flow rate adjustment device 6A is controlled is larger than the amount of refrigerant that circulates when the low-pressure flow rate adjustment device 6B is controlled. Therefore, it is possible to adjust the amount of refrigerant circulating in the refrigerant circuit according to the flow rate adjusting device 6 to be operated, and it is possible to set the optimum amount of refrigerant according to the operation state.

  Here, when the volume of the outdoor heat exchanger 14 and the volume of the indoor heat exchanger 13 are different, the optimum refrigerant amount differs depending on the operation mode. When the volume of the outdoor heat exchanger 14 is larger than the volume of the indoor heat exchanger 13, the optimum refrigerant amount in the cooling mode is larger than the optimum refrigerant amount in the heating mode. Therefore, as shown in FIG. 7, the first receiver 5a is arranged on the outdoor heat exchanger 14 side, and the second receiver 5b is arranged on the indoor heat exchanger 13 side. The first flow rate adjusting device 6a is arranged between the first receiver 5a and the outdoor heat exchanger 14, and the second flow rate adjusting device 6b is arranged between the first receiver 5a and the second receiver 5b.

  When the control device 20 controls the first flow rate adjustment device 6a and fully opens the second flow rate adjustment device 6b in the cooling mode, the refrigerant does not enter and exit the first and second receivers 5a and 5b. The amount of circulating refrigerant becomes large. When the control device 20 controls the second flow rate adjusting device 6b and fully opens the first flow rate adjusting device 6a, the liquid refrigerant is accumulated in the first receiver 5a, and no refrigerant is accumulated in the second receiver 5b. The amount of circulating refrigerant is medium.

  When the control device 20 controls the first flow rate adjustment device 6a and fully opens the second flow rate adjustment device 6b in the heating mode, liquid refrigerant accumulates in the first and second receivers 5a and 5b. The amount of circulating refrigerant is small. When the control device 20 controls the second flow rate adjusting device 6b and fully opens the first flow rate adjusting device 6a, the liquid refrigerant is accumulated in the second receiver 5b, and no refrigerant is accumulated in the first receiver 5a. The amount of circulating refrigerant is medium. Therefore, the amount of refrigerant circulating in the cooling mode can be made larger than the amount of refrigerant circulating in the heating mode.

  When the volume of the indoor heat exchanger 13 is larger than the volume of the outdoor heat exchanger 14, the optimum refrigerant amount in the heating mode is larger than the optimum refrigerant amount in the cooling mode. Therefore, as shown in FIG. 8, the 1st receiver 5a is distribute | arranged to the outdoor heat exchanger side, and the 2nd receiver 5b is distribute | arranged to the indoor heat exchanger side. The first flow rate adjusting device 6a is arranged between the first receiver 5a and the second receiver 5b, and the second flow rate adjusting device 6b is arranged between the first receiver 5a and the indoor heat exchanger 13.

  In the cooling mode, when the control device 20 controls the first flow rate adjusting device 6a and fully opens the second flow rate adjusting device 6b, liquid refrigerant accumulates in the first receiver 5a, and no refrigerant accumulates in the second receiver 5b. Absent. The amount of circulating refrigerant is medium. When the control device 20 controls the second flow rate adjustment device 6b and fully opens the first flow rate adjustment device 6a, liquid refrigerant accumulates in the first and second receivers 5a and 5b. The amount of circulating refrigerant is small.

  In the heating mode, when the control device 20 controls the first flow rate adjusting device 6a and fully opens the second flow rate adjusting device 6b, liquid refrigerant accumulates in the second receiver 5b, and no refrigerant accumulates in the first receiver 5a. Absent. The amount of circulating refrigerant is medium. When the control device 20 controls the second flow rate adjusting device 6b and fully opens the first flow rate adjusting device 6a, no refrigerant accumulates in the first and second receivers 5a and 5b. The amount of circulating refrigerant becomes large. Therefore, the amount of refrigerant circulating in the heating mode can be made larger than the amount of refrigerant circulating in the cooling mode.

(Fourth embodiment)
In the above embodiments, the volumes of the plurality of receivers 5 are the same, but in the present embodiment, the volumes of the receivers 5 are different. In the three receivers 5 shown in FIG. 1, the volume of the first receiver 5A is A, the volume of the second receiver 5B is B, and the volume of the third receiver 5C is C. A, B, and C are different values. Other configurations and operations are the same as those in the first embodiment.

  When the control device 20 controls the high pressure side flow rate adjustment device 6a and fully opens the low pressure side flow rate adjustment device 6b, the liquid refrigerant is accumulated in the first receiver 5A, and the second and third receivers 5B and 5C have no refrigerant. I do not collect. The maximum amount of refrigerant accumulated in the receiver 5 is A. When the control device 20 controls the low pressure side flow rate adjustment device 6B and fully opens the high pressure side flow rate adjustment device 6A, liquid refrigerant is accumulated in the first and second receivers 5A and 5B, and the refrigerant is stored in the third receiver 5C. I do not collect. The maximum amount of refrigerant accumulated in the receiver 5 is A + B.

  In this way, by controlling each flow rate adjusting device 6, the amount of refrigerant circulating varies depending on the volume of each receiver 5. Therefore, the amount of refrigerant circulating in the refrigerant circuit can be finely adjusted according to the flow rate adjusting device 6 to be operated, and the optimum amount of refrigerant according to the operating condition can be obtained.

  In the three receivers 5 shown in FIG. 2, the volume of the first receiver 5a is A, the volume of the second receiver 5b is B, and the volume of the third receiver 5c is C. In the cooling mode, when the control device 20 controls the first flow rate adjusting device 6a and fully opens the second flow rate adjusting device 6b, liquid refrigerant accumulates in the first receiver 5a. The maximum amount of refrigerant accumulated in the receiver 5 is A. When the control device 20 controls the second flow rate adjustment device 6b and fully opens the first flow rate adjustment device 6a, liquid refrigerant accumulates in the first and second receivers 5a and 5b. The maximum amount of refrigerant accumulated in the receiver 5 is A + B.

  When the control device 20 controls the first flow rate adjusting device 6a and fully opens the second flow rate adjusting device 6b in the heating mode, liquid refrigerant accumulates in the second and third receivers 5b and 5c. The maximum amount of refrigerant accumulated in the receiver 5 is B + C. When the control device 20 controls the second flow rate adjusting device 6b and fully opens the first flow rate adjusting device 6a, liquid refrigerant accumulates in the third receiver 5c. The maximum amount of refrigerant accumulated in the receiver 5 is C.

  Thus, when the volumes of the plurality of receivers 5 are different, it is possible to finely adjust the amount of refrigerant circulating in the refrigerant circuit according to the operation mode. Therefore, by controlling each flow rate adjusting device 6, it is possible to easily obtain the optimum refrigerant amount according to the operation state.

(Fifth embodiment)
If the amount of refrigerant circulating through the refrigerant circuit is large at the start of the air conditioning operation, the refrigeration cycle is efficiently stabilized. Therefore, in the present embodiment, as the arrangement order of the receivers 5 having different volumes, the volume of the receiver 5 positioned on the upstream side in the refrigerant flow direction is set smaller than the volume of the other receivers 5 positioned on the downstream side. Other configurations and operations are the same as those in the first embodiment.

  That is, among the plurality of receivers 5 arranged between the condenser 2 and the evaporator 4, the volume of the receiver 5 at a position close to the condenser 2 is minimized, and the receiver 5 at a position close to the evaporator 4. The volume of is maximized. For example, as shown in FIG. 1, when there are three receivers 5, the volume of the first receiver 5A on the upstream side is small, the volume of the second receiver 5B is medium, and the volume of the third receiver 5C on the downstream side is large. Become.

  When the high pressure side flow rate adjustment device 6A is controlled and the low pressure side flow rate adjustment device 6B is fully opened, the refrigerant accumulates in the first receiver 5A. When the low pressure side flow rate adjusting device 6B is controlled and the high pressure side flow rate adjusting device 6A is fully opened, the refrigerant accumulates in the first and second receivers 5A and 5B. In any case, the refrigerant does not accumulate in the downstream receiver 5. Since the receiver 5 in which the refrigerant is stored becomes a receiver 5 having a small and medium volume, the amount of refrigerant stored in all the receivers 5 is smaller than that in the receiver 5 having a large volume, and the amount of refrigerant circulating in the refrigerant circuit is small. Become more.

  Here, at a position close to the condenser 2, since the pressure of the circulating refrigerant is high, the refrigerant tends to accumulate in the receiver 5. However, when increasing the amount of circulating refrigerant, if the volume of the receiver 5 is large, a large amount of refrigerant accumulates. The volume of the receiver 5 on the high pressure side should be small in order to avoid excessive accumulation of refrigerant. Therefore, providing the receiver 5 with a small volume at a position close to the condenser 2 is a suitable arrangement when increasing the amount of refrigerant to be circulated.

  Further, the optimum amount of refrigerant circulating through the refrigerant circuit varies depending on the operating conditions. When the plurality of receivers 5 are arranged in order from the one with the smallest volume, the amount of refrigerant accumulated in all the receivers 5 can be easily calculated according to the flow rate adjusting device 6 to be controlled. Therefore, it is possible to easily control each flow rate adjusting device 6 for optimizing the circulating refrigerant amount.

  By the way, the volume of the indoor and outdoor heat exchangers 13 and 14 is determined at the time of installation. Based on the volume of each of the heat exchangers 13 and 14, it is determined whether a large amount of circulating refrigerant is necessary in the cooling mode or in the heating mode. Based on this, the arrangement order of the receivers 5 having different volumes is determined.

  When the volume of the outdoor heat exchanger 14 is larger than the volume of the indoor heat exchanger 13, the amount of refrigerant required in the cooling mode is larger than that in the heating mode. At this time, in the three receivers 5 shown in FIG. 2, the volume of the first receiver 5a is small, the volume of the second receiver 5b is medium, and the volume of the third receiver 5c is large.

  In the cooling mode, when the first flow rate adjusting device 6a is controlled and the second flow rate adjusting device 6b is fully opened, liquid refrigerant accumulates in the first receiver 5a. When the second flow rate adjusting device 6b is controlled and the first flow rate adjusting device 6a is fully opened, liquid refrigerant accumulates in the first and second receivers 5a and 5b. In any case, no refrigerant accumulates in the third receiver 5c.

  In the heating mode, when the first flow rate adjusting device 6a is controlled and the second flow rate adjusting device 6b is fully opened, liquid refrigerant accumulates in the second and third receivers 5b and 5c. When the second flow rate adjusting device 6b is controlled and the first flow rate adjusting device 6a is fully opened, liquid refrigerant accumulates in the third receiver 5c.

  In the cooling mode, liquid refrigerant accumulates in the receiver 5 having a small and medium volume, and in the heating mode, liquid refrigerant accumulates in the receiver 5 having a medium and large volume. Therefore, the amount of refrigerant stored in the receiver 5 is large during the heating mode, decreases during the cooling mode, and the amount of refrigerant circulating in the refrigerant circuit during the cooling mode is greater than during the heating mode.

  When the volume of the indoor heat exchanger 13 is larger than the volume of the outdoor heat exchanger 14, the amount of refrigerant required in the heating mode is larger than that in the cooling mode. At this time, in the three receivers 5 shown in FIG. 2, the volume of the third receiver 5c is small, the volume of the second receiver 5b is medium, and the volume of the first receiver 5a is large.

  In the heating mode, when the second flow rate adjusting device 6b is controlled and the first flow rate adjusting device 5a is fully opened, the liquid refrigerant is accumulated in the third receiver 5c. When the first flow rate adjusting device 6a is controlled and the second flow rate adjusting device 6b is fully opened, liquid refrigerant accumulates in the second and third receivers 5b and 5c.

  In the cooling mode, when the first flow rate adjusting device 6a is controlled and the second flow rate adjusting device 6b is fully opened, liquid refrigerant accumulates in the first receiver 5a. When the second flow rate adjusting device 6b is controlled and the first flow rate adjusting device 6a is fully opened, liquid refrigerant accumulates in the first and second receivers 5a and 5b.

  In the heating mode, liquid refrigerant accumulates in the receiver 5 having a small and medium volume, and in the cooling mode, liquid refrigerant accumulates in the receiver 5 having a medium and large volume. Therefore, the amount of refrigerant stored in the receiver 5 is large in the cooling mode, decreases in the heating mode, and the amount of refrigerant circulating in the refrigerant circuit in the heating mode is larger than in the cooling mode.

  When the number of the receivers 5 is two and the volume of the outdoor heat exchanger 14 is larger than the volume of the indoor heat exchanger 13, the volume of the first receiver 5a shown in FIG. 7 is small and the volume of the second receiver 5b is large. It is said. In the cooling mode, when the second flow rate adjusting device 6b is controlled and the first flow rate adjusting device 6a is fully opened, liquid refrigerant is accumulated in the first receiver 5a. When the first flow rate adjusting device 6a is controlled and the second flow rate adjusting device 6b is fully opened, no refrigerant accumulates in each receiver 5a, 5b.

  In the heating mode, when the second flow rate adjusting device 6b is controlled and the first flow rate adjusting device 6a is fully opened, the liquid refrigerant is accumulated in the second receiver 5b. When the first flow rate adjusting device 6a is controlled and the second flow rate adjusting device 6b is fully opened, liquid refrigerant accumulates in the first and second receivers 5a and 5b. Even in this case, the amount of refrigerant circulating in the refrigerant circuit in the cooling mode is larger than that in the heating mode.

  When the volume of the indoor heat exchanger 13 is larger than the volume of the outdoor heat exchanger 14, the volume of the second receiver 5b shown in FIG. 8 is small and the volume of the first receiver 5a is large. In the cooling mode, when the first flow rate adjusting device 6a is controlled and the second flow rate adjusting device 6b is fully opened, the liquid refrigerant is accumulated in the second receiver 5b. When the second flow rate adjusting device 6b is controlled and the first flow rate adjusting device 6a is fully opened, liquid refrigerant accumulates in the first and second receivers 5a and 5b.

  In the heating mode, when the second flow rate adjusting device 6b is controlled and the first flow rate adjusting device 6a is fully opened, no refrigerant is accumulated in the receivers 5a and 5b. When the first flow control device 6a is controlled and the second flow control device 6b is fully opened, the liquid refrigerant is accumulated in the second receiver 5b. Even in this case, the amount of refrigerant circulating in the refrigerant circuit in the heating mode is larger than that in the cooling mode.

(Sixth embodiment)
During the air conditioning operation, the flow rate adjusting device is controlled in accordance with an operation state such as a change in superheat degree. According to the control of the flow rate adjusting device 6, the amount of refrigerant accumulated in the receiver 5 varies, and the refrigerant circulating in the refrigerant circuit is adjusted. When the flow control device 6 is fully opened, the amount of refrigerant passing through the flow control device 6 increases.

  By the way, pressure loss occurs when the refrigerant passes through the flow control device 6. As the flow rate adjusting device 6 increases, the pressure loss also increases. When the pressure loss increases, the refrigerant hardly flows into the evaporator 4 and the degree of superheat increases. Therefore, the discharge temperature from the compressor 1 rises, the air conditioning capability is insufficient, and the operation efficiency is deteriorated. The refrigerant flowing into the evaporator 4 can be increased by increasing the opening degree of the flow rate adjusting device 6.

  However, when the flow control device 6 is fully open or close to full open, if a situation occurs in which the amount of circulating refrigerant is insufficient, the amount of circulating refrigerant is increased even if the flow control device 6 is opened further. I can't. That is, it cannot be dealt with by the control of the flow rate adjusting device 6.

  In this embodiment, in such a case, the flow rate adjusting device 6 is made controllable by adjusting the rotation speed of the compressor 1 so that the refrigerant amount can be adjusted. That is, when the opening degree of the plurality of flow rate adjusting devices 6 becomes equal to or larger than the predetermined opening degree, the control device 20 decreases the rotational speed of the compressor 1.

  As shown in FIG. 9, two flow control devices 6a and 6b are provided between the outdoor heat exchanger 14 and the indoor heat exchanger 13 of the refrigerant circuit, and the first flow control device 6a and the second flow control device 6b. Between the two, one receiver 5 is provided. The other configurations and operations are the same as those in the above embodiments except that there is one receiver 5.

  When the air conditioning operation is performed, the control device 20 controls each flow rate adjusting device 6 after confirming that the refrigeration cycle is stable. For example, in the cooling mode, the second flow rate adjusting device 6b is fully opened, and the opening degree of the first flow rate adjusting device 6a is set to the set opening degree. And the 1st flow regulating device 6a is controlled according to an operation situation. When the degree of superheat increases, the control device 20 controls the first flow rate adjusting device 6a so that the opening degree of the first flow rate adjusting device 6a increases. The amount of refrigerant passing through the first flow rate adjusting device 6a increases, the amount of refrigerant flowing into the indoor heat exchanger 13 increases, and the degree of superheat decreases.

  During the air-conditioning operation, the control device 20 changes the opening degree of the flow rate adjusting device 6 according to the operating condition such as the degree of superheat in order to adjust the circulating refrigerant amount, but the refrigerant amount is adjusted by the control of the flow rate adjusting device 6. Determine if it is possible.

  That is, as shown in FIG. 10, the control device 20 checks whether the opening degree of the first and second flow rate adjusting devices 6a and 6b is equal to or larger than a predetermined opening degree (S1). The predetermined opening is an opening close to full opening, and is set to 80%, for example. In addition, although the 2nd flow volume adjustment apparatus 6b is fully opened, the opening degree of the 2nd flow volume adjustment apparatus 6b should just be more than a predetermined opening degree. When the opening degree of the first flow rate adjusting device 6a becomes equal to or larger than the predetermined opening degree, the control device 20 determines that it is impossible to adjust the refrigerant amount under the control of the flow rate adjusting device 6, and the rotation of the compressor 1 The compressor 1 is controlled so as to decrease the number (S2). For example, the rotation speed of the compressor 1 is reduced by 500 rpm.

  When the rotation speed of the compressor 1 decreases, the optimum refrigerant amount corresponding to the rotation speed of the compressor 1 decreases. Therefore, the control device 20 changes the opening degree of the first flow rate adjusting device 6a according to the rotational speed of the compressor 1 (S3). The opening degree of the first flow rate adjusting device 6a becomes an opening degree corresponding to the reduced rotational speed, and the opening degree of the first flow rate adjusting device 6a becomes small. The control device 20 checks whether the changed opening is equal to or greater than a predetermined opening (S2). When the opening degree is equal to or greater than the predetermined opening degree, the control device 20 controls the compressor 1 again to lower the rotational speed of the compressor 1 by, for example, 500 rpm. As the rotational speed of the compressor 1 decreases, the opening of the first flow rate adjusting device 6a is changed to be smaller.

  When the opening degree of the first flow rate adjusting device 6a becomes smaller than the predetermined opening degree, as shown in FIG. 11, the controller 20 checks whether or not the room temperature has become higher than the set temperature after a certain time has passed ( S4). When the room temperature is higher than the set temperature, the control device 20 controls the compressor 1 so as to increase the rotational speed of the compressor 1 (S5). For example, the rotation speed of the compressor 1 is increased by 500 rpm. The control apparatus 20 changes the opening degree of the 1st flow volume adjustment apparatus 6a according to the rotation speed of the compressor 1 (S6). The opening degree of the first flow rate adjusting device 6a is an opening degree corresponding to the increased rotational speed of the compressor 1, and the opening degree of the first flow rate adjusting device 6a is increased. Thereafter, the control device 20 checks whether the opening degree of the first and second flow rate adjusting devices 6a and 6b is equal to or larger than a predetermined opening degree (S1).

  When the air conditioning load is large, even if each flow rate adjusting device 6 becomes fully open or close to full open and cannot be controlled any more, the number of rotations of the compressor 1 is decreased, so that the number of rotations of the compressor 1 is reduced. The optimum amount of refrigerant is reduced. Accordingly, the flow rate adjusting device 6 has an opening degree corresponding to the reduced rotational speed, and the opening amount of the first flow rate adjusting device 6a becomes small, so that the flow rate adjusting device 6 can be controlled. That is, when the degree of superheat increases, the opening degree of the flow rate adjusting device 6 can be increased by the above control. By changing to the opening degree of the flow rate adjusting device 6, the liquid refrigerant accumulated in the receiver 5 is discharged to the refrigerant circuit, and the amount of circulating refrigerant increases and the degree of superheat can be reduced. Therefore, it can be adjusted to the optimum refrigerant amount by the control of the flow rate adjusting device 6.

  When the air conditioning load is small, a sufficient air conditioning load can be obtained by performing the above control even if the amount of circulating refrigerant is reduced. Therefore, the rotation speed of the compressor 1 can be lowered, and power saving of the air conditioner can be achieved. When the air conditioning load is large, the amount of refrigerant circulating can be increased by performing the above control, and an appropriate degree of superheat can be maintained. For this reason, air conditioning capability is high and efficient air conditioning operation can be performed.

  Also, especially in a specific environment where the humidity is high and the outside air temperature is high, the air conditioning load increases, so the amount of circulating refrigerant must be increased. However, even if the flow control device 6 is fully opened, the refrigerant flows into the evaporator 4 due to pressure loss when the refrigerant passes through the flow control device 6, and temperature unevenness occurs in the evaporator 4. When a gas refrigerant having substantially the same temperature as room temperature flows into the indoor heat exchanger 13 that is the evaporator 4, moisture contained in the sucked indoor air flows to the outlet without being sufficiently condensed in the indoor heat exchanger 13. When the air passes through the air outlet, dew is attached to the wall of the air outlet. The accumulated dew is blown out by the blown wind, and water is scattered from the outlet into the room.

  In such a specific environment, by performing the above-described control when the air conditioning load is large, the circulation amount of the refrigerant is adjusted so that the flow rate adjusting device 6 can be operated within a controllable range without being almost fully opened. Can do. Thereby, the refrigerant shortage can be solved. Therefore, since the temperature unevenness does not occur in the evaporator 4, it is possible to prevent dew condensation and water scattering.

  The above control is also performed when the air conditioning operation is performed in the heating mode. The flow rate adjusting device 6 can be controlled according to the air conditioning load, and can be adjusted to the optimum refrigerant amount. Further, when there are a plurality of flow rate adjusting devices 6, the pressure loss is larger than when there is one flow rate adjusting device 6, but by performing the same control as described above, it is possible to eliminate the shortage of the refrigerant amount, Efficient air conditioning operation can be performed.

  Also, in the refrigerant circuit in which a plurality of receivers 5 are provided and a plurality of flow rate adjusting devices 6 are provided in accordance with each receiver 5, when all the flow rate adjusting devices 6 have reached a predetermined opening degree or more, Similar control is performed.

(Seventh embodiment)
As described above, during the air conditioning operation in the cooling mode, the air conditioning load increases in a specific environment with high humidity and high outside air temperature. In order to increase the air conditioning capacity, the amount of circulating refrigerant must be increased. However, even when the flow rate adjusting device 6 is fully opened or close to full open, there is a problem that the refrigerant is insufficient in the indoor heat exchanger 13 due to pressure loss when the refrigerant passes through the flow rate adjusting device 6 and dew is attached to the outlet. Arise. Therefore, in the present embodiment, in order to prevent such dew, the control device 20 performs dew prevention control. Other configurations and operations are the same as those in the sixth embodiment.

  When the air conditioning operation is performed in the cooling mode, the control device 20 controls the first and second flow rate adjusting devices 6a and 6b based on the change in the degree of superheat. The second flow rate adjusting device 6b is fully opened, and the opening degree of the first flow rate adjusting device 6a changes. As shown in FIG. 12, when the air conditioning load is increased and the amount of circulating refrigerant is large (S10), the first flow rate adjusting device 6a is fully opened (S11). The control device 20 confirms that the opening degree of each of the flow rate adjusting devices 6a and 6b is not less than a predetermined opening degree, for example, 80% or more, starts dew prevention control, and sets the rotation speed of the compressor 1. The compressor 1 is controlled to be lowered (S12). And the control apparatus 20 controls the fan 15 so that the rotation speed of the fan 15 for outdoor heat exchangers may be lowered | hung (S13).

  When the control device 20 changes the opening degree of the first flow rate adjusting device 6a in accordance with the decrease in the rotational speed of the compressor 1, the opening degree of the first flow rate adjusting device 6a becomes smaller. The optimum amount of refrigerant also decreases according to the rotational speed of the compressor 1. Since the first flow rate adjustment device 6a can be controlled so that the opening degree can be increased, the opening degree of the first flow rate adjustment device 6a can be increased even if the air conditioning load is large. By increasing the opening degree of the first flow rate adjusting device 6a, the amount of circulating refrigerant increases, and the amount of refrigerant can be optimally adjusted even in a situation where the air conditioning load is large. As a result, the shortage of refrigerant in the indoor heat exchanger 13 can be solved, temperature unevenness does not occur in the indoor heat exchanger 13, and dew condensation can be prevented.

  At the same time as the rotation speed of the compressor 1 is decreased, the rotation speed of the fan 15 for the outdoor heat exchanger is decreased, so that the wind speed toward the outdoor heat exchanger 14 is weakened, and the heat radiation of the refrigerant in the outdoor heat exchanger 14 is decreased. By reducing the amount of refrigerant that accumulates in the outdoor heat exchanger 14, the amount of refrigerant that circulates increases, and the shortage of refrigerant can be compensated. Compared with the case where only the rotational speed of the compressor 1 is reduced, the amount of circulating refrigerant can be increased. That is, even if the amount of decrease in the rotational speed of the compressor 1 is reduced, it is possible to secure an amount of refrigerant that can solve the shortage of refrigerant. Since the air conditioning capacity is proportional to the rotational speed of the compressor 1, the smaller the decrease in the rotational speed of the compressor 1, the lower the decrease in the air conditioning capacity. Therefore, sufficient refrigerant flows through the indoor heat exchanger 13, the degree of superheat can be reduced, and the air conditioning operation can be performed efficiently even when the air conditioning load is large.

  In the above description, when the opening degree of each flow rate adjustment device 6 becomes fully open or close to full open, the control device 20 determines that the amount of circulating refrigerant is large and starts dew prevention control. Instead, when the air conditioning load is large, the control device 20 may detect that the amount of circulating refrigerant is large and perform dew prevention control. That is, in the cooling mode, the control device 20 detects the outside air temperature and the temperature of the indoor heat exchanger 13, and determines whether the amount of the circulating refrigerant is large based on these information. When the outside air temperature is equal to or higher than the predetermined temperature and the temperature of the evaporator 4 (indoor heat exchanger 13) or the discharge temperature or the suction temperature of the compressor 1 is equal to or higher than the predetermined temperature, the control device 20 has a large amount of refrigerant to circulate. It is judged that. When this state is reached, the opening degree of each flow rate adjusting device 6 is greater than or equal to a predetermined opening degree.

  Further, when the degree of superheat increases and the opening degree of the flow rate adjusting device 6 becomes fully open or close to full open, only the rotational speed of the fan for the condenser 2 may be lowered. Since the heat exchange capability of the condenser 2 is reduced, the amount of refrigerant accumulated in the condenser 2 is reduced, and the amount of circulating refrigerant can be increased. Therefore, not only in the cooling mode but also in the heating mode, the circulating refrigerant amount can be adjusted without opening the flow rate adjusting device 6 to near full open. In addition, you may make it reduce the rotation speed of the fan for the condenser 2 simultaneously with the rotation speed of the compressor 1 falling. Thereby, not only in the cooling mode but also in the heating mode, the amount of circulating refrigerant can be adjusted without opening the flow rate adjusting device 6 to near full open.

(Eighth embodiment)
The refrigerant circulating in the refrigerant circuit enters and exits the receiver 5 through the connecting pipe 8 connected to the connection pipe 7 of the refrigerant circuit. Depending on the pressure difference between the pressure of the refrigerant in the connection pipe 7 and the pressure in the receiver 5, the refrigerant enters the receiver 5 from the connecting pipe 8 and accumulates, or the accumulated refrigerant is discharged from the receiver 5. The refrigerant cannot smoothly enter and exit from the receiver 5 only with this pressure difference. When the temperature of the receiver 5 is higher than the temperature of the refrigerant, the pressure in the receiver 5 increases, the refrigerant becomes difficult to flow into the receiver 5, and the refrigerant does not accumulate. When the temperature of the receiver 5 is lower than the temperature of the refrigerant, the pressure in the receiver 5 decreases, the refrigerant becomes difficult to get out of the receiver 5, and the refrigerant in the receiver 5 does not decrease.

  Therefore, in the present embodiment, the receiver 5 is warmed or cooled so that the refrigerant can smoothly enter and exit the receiver 5. As shown in FIGS. 13 and 14, a cooling pipe 30 that cools the receiver 5 by diverting a low-temperature refrigerant from the refrigerant circuit, and a heating pipe 31 that warms the receiver 5 by diverting a high-temperature refrigerant from the refrigerant circuit are provided. It is done. The heating pipe 31 is connected to a discharge side pipe of the compressor 1, and the cooling pipe 30 is connected to a suction side pipe of the compressor 1. The cooling pipe 30 and the heating pipe 31 are wound around the receiver 5 so as not to contact each other. Other configurations and operations are the same as those in the above embodiments.

  The cooling pipe 30 and the heating pipe 31 are each formed from a single capillary tube and have a smaller diameter than the piping of the refrigerant circuit. One end and the other end of the cooling pipe 30 communicate with the piping of the refrigerant circuit, respectively, and cooling valves 32 for opening and closing the cooling pipe 30 are provided on one end side and the other end side, respectively. Similarly, one end and the other end of the heating pipe 31 communicate with the piping of the refrigerant circuit, respectively, and heating valves 33 for opening and closing the heating pipe 31 are provided on one end side and the other end side, respectively.

  The cooling valve 32 and the heating valve 33 are controlled by the control device 20 according to the operating situation. When the two cooling valves 32 are simultaneously opened, a low-temperature refrigerant flows through the cooling pipe 30. When the two cooling valves 32 are closed, no refrigerant flows through the cooling pipe 30. Further, when the two heating valves 33 are opened simultaneously, a high-temperature refrigerant flows through the heating pipe 31. When the two heating valves 33 are closed, no refrigerant flows through the heating pipe 31.

  When storing the refrigerant in the receiver 5, the control device 20 opens the cooling valve 32 and closes the heating valve 33. The low-temperature refrigerant sucked into the compressor 1 flows into the cooling pipe 30 and the receiver 5 is cooled. The gas refrigerant in the receiver 5 is liquefied, the pressure in the receiver 5 is lowered, and the difference between the pressure on the piping side of the refrigerant circuit and the pressure in the receiver 5 is increased. As the pressure difference increases, the refrigerant smoothly flows into the receiver 5 and accumulates quickly. Therefore, the amount of circulating refrigerant can be quickly reduced.

  When discharging the refrigerant from the receiver 5, the control device 20 closes the cooling valve 32 and opens the heating valve 33. The high-temperature refrigerant discharged from the compressor 1 flows into the heating pipe 31, and the receiver 5 is warmed. The liquid refrigerant in the receiver 5 evaporates, the pressure in the receiver 5 increases, and the difference between the pressure in the receiver 5 and the piping side of the refrigerant circuit increases. As the pressure difference increases, the refrigerant flows out of the receiver 5 smoothly and is discharged quickly. Therefore, the amount of circulating refrigerant can be increased quickly.

  The cooling pipe 30 and the heating pipe 31 are very thin tubes. Even if the refrigerant flows from the piping of the refrigerant circuit to the respective pipes 30 and 31, the amount of the circulating refrigerant is reduced only slightly. Therefore, the temperature of the receiver 5 can be adjusted without affecting the air conditioning capability. Then, by adjusting the temperature of the receiver 5 in conjunction with the control of the flow rate adjusting device 6, the refrigerant flows into and out of the receiver 5 smoothly, and the amount of circulating refrigerant can be adjusted quickly and optimally.

  Even when the refrigerant circuit has a plurality of receivers 5, the cooling pipe 30 and the heating pipe 31 may be wound around each receiver 5. Moreover, the cooling valve 32 and the heating valve 33 are kept closed with respect to the receiver 5 in which a refrigerant | coolant does not enter / exit among several receivers 5. FIG. Thereby, it is not necessary to reduce the refrigerant circulating through the refrigerant circuit.

  By the way, as described in Japanese Utility Model Publication No. 59-118984, it is conceivable to directly wrap the pipe of the refrigerant circuit around the receiver 5. However, only the refrigerant having a temperature corresponding to the operation mode flows, and the high-temperature refrigerant and the low-temperature refrigerant cannot be switched according to the operation state, which is not suitable for adjusting the refrigerant amount.

(Ninth embodiment)
The receiver 5 is disposed in a gap in the outdoor unit 11. When deciding the arrangement of the receiver 5, consideration must be given so that the receiver 5 and the connecting pipe 8 do not interfere with the piping and components in the outdoor unit 11. On the other hand, the size and shape of the receiver 5 are determined in order to ensure a predetermined volume of the receiver 5. However, in the outdoor unit 11, there is only a limited gap due to the structure, and in order to arrange the receiver 5 so as not to interfere, the layout of piping and parts is changed, or the outdoor unit 11 is enlarged. Thus, it is necessary to secure a gap in which the receiver 5 can be disposed.

  Therefore, in the present embodiment, the receiver 5 includes a plurality of tanks 40 as shown in FIGS. Here, one receiver 5 is composed of three tanks 40. Other configurations and operations are the same as those in the above embodiments.

  The tank 40 is a cylindrical container, and an entrance is formed on the bottom surface. The tanks 40 have the same shape. The total volume of the three tanks 40 is the same as the volume of one receiver 5. Each tank 40 is located in a gap in the outdoor unit 11 and is shifted and arranged without contacting each other. As shown in FIG. 17, the three tanks 40 are respectively connected to one connecting pipe 8 through branch pipes 41. A branch pipe 41 is connected to the lower surface of the tank 40, and the branch pipe 41 is connected to the connecting pipe 8. The tank 40 is located higher than the branch pipe 41, and the vertical positions of the branch pipes 41 are different.

  When the refrigerant is stored in the receiver 5, the refrigerant flows from the pipe of the refrigerant circuit into the connecting pipe 8 and enters the tank 40 through the branch pipe 41 connected to the lowest position. Subsequently, the refrigerant enters the other tank 40 from the branch pipe 41 connected to a position higher than the branch pipe 41. The refrigerant accumulates in order from the tank 40 connected to the branch pipe 41 at the lower position.

  When the refrigerant is discharged from the receiver 5, the higher the position of the refrigerant is, the higher the potential energy is. Therefore, the refrigerant stored in the tank 40 at the highest position is discharged first. The refrigerant is sequentially discharged from the tank 40 at a high position.

  Thus, since the tank 40 is smaller than the receiver 5, the gap that can accommodate the tank 40 may be small. Therefore, the choice of the position where the tank 40 can be arranged increases. Therefore, the receiver 5 can be arranged according to the gap without changing the arrangement of the pipes and components in the outdoor unit 11. Moreover, since it is not necessary to form a large gap for the receiver 5, the outdoor unit 11 can be downsized.

  In addition, gaps are inevitably formed depending on the layout of piping and parts, but the shapes of the gaps are various. Therefore, the shape of the tank 40 may be changed according to the shape of the gap. For example, as shown in FIG. 18, the tank 40 is formed in an L shape. Thereby, the space which can install the tank 40 increases, the space in the outdoor unit 11 can be utilized effectively, and the outdoor unit 11 can be further reduced in size.

  Even when there are a plurality of receivers 5, each receiver 5 may be configured with a plurality of tanks 40. Note that it is not necessary to configure all the receivers 5 from a plurality of tanks 40. If there is a gap in which the receivers 5 can be installed, the receivers 5 may be used as they are.

(Tenth embodiment)
In an air conditioner having a receiver 5 for storing refrigerant and a plurality of flow rate adjusting devices 6a and 6b for adjusting the amount of refrigerant stored in the receiver 5 in order to adjust the amount of refrigerant circulating in the refrigerant circuit, as shown in FIG. The control device 20 that controls the flow rate adjusting devices 6a and 6b controls the opening degree of the flow rate adjusting devices 6a and 6b so that the refrigerant amount circulating in the refrigerant circuit becomes the optimum refrigerant amount according to the air conditioning operation.

  Here, when the air conditioning operation is started, the compressor 1 is driven, and the refrigerant circulates through the refrigerant circuit to form a refrigeration cycle. The target rotational speed of the compressor 1 is set based on the set temperature and the room temperature, and the initial opening degree of each flow rate adjusting device 6a, 6b is determined according to the target rotational speed.

  When the air conditioning operation is started, the flow rate adjusting devices 6a and 6b are opened to the initial opening degree, and the compressor 1 is driven at the target rotational speed. The refrigerant discharged from the compressor 1 circulates through the refrigerant circuit, and after a while, the refrigeration cycle is stabilized. Thereafter, the rotation speed of the compressor 1 is changed according to the room temperature or the outside air temperature, the opening degree of each flow rate adjusting device 6a, 6b is changed according to the rotation speed of the compressor 1, and the amount of circulating refrigerant is optimized. It is adjusted to become.

  The controller 20 performs refrigerant amount adjustment control after confirming that the refrigeration cycle is stable. Conventionally, as described in Japanese Patent No. 3334507, the stability of the refrigeration cycle is determined based on whether or not the discharge temperature of the refrigerant from the compressor 1 is equal to or higher than a predetermined temperature. However, the discharge temperature also changes due to a change in the outside air temperature or a change in the rotation speed of the compressor 1. Therefore, even though the refrigeration cycle is not yet stable, the discharge temperature may reach a predetermined temperature, and an erroneous determination is made. As a result, it takes extra time to reach the optimum refrigerant amount.

  Therefore, in the present embodiment, the control device 20 determines whether or not the refrigeration cycle is stable using a mathematical expression that represents a change in the discharge temperature of the compressor 1 so that it can be strictly determined that the refrigeration cycle is stable. Then, the opening degree of the flow rate adjusting device 6 is controlled after the refrigeration cycle is stabilized. At this time, a plurality of mathematical expressions are prepared using the rotation speed of the compressor 1 as a parameter, and the control device 20 selects a mathematical expression to be used for determination according to the rotation speed of the compressor 1.

  The determination of the stability of the refrigeration cycle is made based on the change over time in the discharge temperature from the compressor 1. The mathematical formula used for this determination is an approximate formula obtained from the result of measuring the change in discharge temperature over time, and the rotational speed of the compressor 1, the discharge temperature, and the outside air temperature are taken into account in the mathematical formula. The discharge temperature is the surface temperature of the discharge pipe connected to the outlet side of the compressor 1.

  FIG. 19 shows a flow of stability determination processing. First, the time change of the discharge temperature of the compressor 1 is actually measured, and the approximate expression A1 is created from the preset numerical expression A and the actual measurement value (S20). This approximate expression A1 is stored in the memory of the control device 20. When the air conditioning operation is started, the control device 20 inputs the detected outside air temperature and the rotation speed of the compressor 1 to the approximate expression A1 (S21). The control device 20 determines whether or not the degree of time change of the temperature difference ΔT between the discharge temperature of the compressor 1 and the outside air temperature is within a predetermined value δ (S22). When this process is repeated and the degree of time change of the temperature difference ΔT is within the range of the predetermined value δ, the control device 20 determines that the refrigeration cycle is stable (S23), and performs the stability determination process. finish.

  Next, a specific procedure for creating an approximate expression is shown. In the present embodiment, approximate expressions are created for different rotational speeds.

(Step 1)
At the outside air temperature Tout1, the stable discharge temperature when the compressor 1 is rotated at the rotation speeds f1 and f2 and the discharge temperature when the compressor 1 is rotated at the rotation speeds f1 and f2 are measured. FIG. 20A shows the change over time in the discharge temperature at the rotation speeds f1 and f2. The vertical axis represents the temperature difference ΔT between the discharge temperature and the outside air temperature, and the horizontal axis represents time t. In the figure, ΔT1 is the stable discharge temperature Td11-Tout at the rotation speed f1, and ΔT2 is the stable discharge temperature Td12-Tout at the rotation speed f2. Tout is an arbitrary outside temperature. As is apparent from the plotted actual measurement values, the temperature difference function ΔT (t) converges to ΔT1 and ΔT2 with time. Moreover, since discharge temperature becomes high, so that the rotation speed of the compressor 1 is high, the temperature difference when the rotation speed is high becomes larger than the temperature difference when the rotation speed is low.

(Step 2)
Formulas relating to changes in the discharge temperature over time are set in advance and stored in the memory of the control device 20. Formulas A and a are created for each rotation speed.
ΔT (t) = {ΔT2 + (ΔT1−ΔT2) × (f−f2) / (f1−f2)}
X {1-e ^{(-t / τ1)} } (Formula A)
ΔT (t) = {ΔT2 + (ΔT1−ΔT2) × (f−f2) / (f1−f2)}
X {1-e ^{(-t / τ2)} } (Formula a)
f: Arbitrary rotational speed τ1, τ2: parameter In Formula A, if f = f1,
ΔT (t) = ΔT1 × {1-e ^{(−t / τ1)} } (Expression A ′)
In formula a, if f = f2,
ΔT (t) = ΔT2 × {1-e ^{(−t / τ2)} } (Expression a ′)

(Step 3)
Parameters τ1 and τ2 are determined by the measurement result in step 1 and the least square method. As shown in FIG. 20B, the slope of the saturation curve of ΔT (t) varies greatly depending on the value of the parameter τ. From this figure, a curve of τ = 3.5 is given as a curve that most closely approximates the plotted measurement values. Further, when the rotation speed of the compressor 1 is different, the value of the parameter τ is different.

The values determined by the procedure so far are substituted into Formula A and Formula a, and the underlined portion of Formula A and Formula a below is determined.
ΔT (t) = {ΔT2 + (ΔT1−ΔT2) × (f−f2) / (f1−f2)}
X {1-e ^{(-t / τ1)} } (Formula A)
ΔT (t) = {ΔT2 + (ΔT1−ΔT2) × (f−f2) / (f1−f2)}
X {1-e ^{(-t / τ2)} } (Formula a)
FIG. 20C shows a saturation curve of the formula A. It can be seen that the saturation curve changes depending on the rotational speed of the compressor 1.

(Step 4)
When the outside air temperature is Tout2, the stable discharge temperature when the compressor 1 is rotated at the rotation speeds f1 and f2, and the stable discharge temperature Td21 and Td22 when the compressor 1 is rotated at the rotation speeds f1 and f2 are Measured. The outside air temperature affects the discharge temperature. Therefore, by correcting ΔT1 and ΔT2 in the expressions A and a based on the change degree of the discharge temperature due to the outside air temperature, the influence of the outside air temperature can be eliminated, and an accurate approximate expression for the time change of the discharge temperature can be obtained. It is done.

(Step 5)
The measurement result at the rotation speed f1 in step 4 is substituted into equation B. Further, the measurement result at the rotation speed f2 is substituted into the expression C.
ΔT1 = Td11 + (Td21−Td11)
× (Tout-Tout1) / (Tout2-Tout1)
−Tout1 Formula B
ΔT2 = Td12 + (Td22−Td12)
× (Tout-Tout1) / (Tout2-Tout1)
−Tout1 Formula C
Expressions B and C are substituted into Expression A and Expression a, respectively, and approximate expressions A1 and a1 are obtained.
ΔT (t) = {ΔT2 + (ΔT1−ΔT2) × (f−f2) / (f1−f2)}
X {1-e ^{(-t / τ1)} } (Formula A1)
ΔT (t) = {ΔT2 + (ΔT1−ΔT2) × (f−f2) / (f1−f2)}
X {1-e ^{(-t / τ2)} } (Formula a1)
Expressions B and C are used for ΔT1 and ΔT2 in the above expressions. FIG. 21A shows that the discharge temperature saturation curve changes depending on the outside air temperature.

  The two approximate expressions obtained as described above correspond to the rotational speed of the compressor 1. That is, the approximate expression a1 corresponds to a high rotation range where the rotation speed of the compressor 1 is higher than the predetermined rotation speed, and the approximate expression A1 corresponds to a low rotation speed range lower than the predetermined rotation speed.

  These approximate expressions are stored in the memory of the control device 20 and are used to determine the stability of the refrigeration cycle. That is, when starting the air conditioning operation, the control device 20 substitutes the rotation speed of the compressor 1 and the detected outside air temperature into one of the approximate equations selected from the two approximate equations, and each time since the start of the operation. Calculate the temperature difference. The rotational speed of the compressor 1 is acquired by detecting the rotational speed of the motor of the compressor 1 or is acquired based on the operating frequency output when the compressor 1 is driven.

  And the control apparatus 20 calculates the timing when the change of the calculated temperature difference becomes small. It is determined that the timing at which the change in the temperature difference becomes small is when the refrigeration cycle is stabilized. The control device 20 derives the time when this timing is reached from the approximate expression. This time is defined as a stabilization time required from the start of operation to stabilization. The control device 20 determines that the refrigeration cycle is stable when the stable time is reached after starting the operation, and performs refrigerant amount adjustment control.

  When the outside air temperature changes before reaching the stable time, the control device 20 performs the calculation again to correct the stable time. When the rotational speed of the compressor 1 is changed, the stabilization time is similarly corrected.

  Specifically, in Formula A1 or Formula a1 into which an arbitrary rotation speed f and outside air temperature Tout are respectively substituted, it is determined that the refrigeration cycle is stable when the time change rate of ΔT (t) becomes smaller than the threshold δ. (See FIG. 21B). The threshold δ is, for example, ± 0.1 ° C./min. This threshold value is merely an example, and is not limited to this.

  Here, one of the two approximate expressions is selected according to the rotational speed of the compressor 1. One approximate expression a1 corresponds to the high rotation range, and the other approximate expression A1 corresponds to the low rotation range. The control device 20 determines whether the rotation speed during operation is in a high rotation range or a low rotation range, and selects an approximate expression corresponding to the rotation range. In this way, a more rigorous determination can be made by properly using the approximate expression used for the determination of stability according to the rotational speed of the compressor 1. In addition, the determination of stability is not performed based on the discharge temperature of the compressor 1 detected during operation. Therefore, the stability can be determined without being influenced by the actual change in the discharge temperature, and the reliability of the determination is increased.

  Note that the number of approximate equations used for the determination may be two or more. A plurality of rotation ranges are set with respect to the rotation speed of the compressor 1, and a plurality of approximate expressions correspond to the respective rotation ranges. An approximate expression is selected according to the rotation range to which the rotation speed during operation belongs. Further, the number of receivers 5 is not limited to one, and a plurality of receivers 5 may be used.

  As described above, the air conditioner of the present invention includes a refrigerant circuit in which the compressor 1, the condenser 2, the throttle unit 3, and the evaporator 4 are connected by piping. The throttling unit 3 includes a plurality of receivers 5 that store refrigerant and a plurality of flow rate adjusting devices 6 that adjust the amount of refrigerant stored in each receiver 5 in order to adjust the amount of refrigerant circulating in the refrigerant circuit.

  The amount of refrigerant circulating in the refrigerant circuit varies depending on the amount of refrigerant accumulated in each receiver 5. Therefore, by operating the flow rate adjusting device 6 according to the operating state, the refrigerant amount accumulated in each receiver 5 is adjusted, and the optimum refrigerant amount according to the operating state can be obtained.

  A plurality of flow rate adjusting devices 6 are arranged in series in the refrigerant circuit, a receiver 5 is connected between the adjacent flow rate adjusting devices 6, and the flow rate adjusting device 6 located downstream of the receiver 5 in the refrigerant flow direction operates. As a result, the amount of refrigerant accumulated in the receiver 5 changes.

  The operation of the flow rate adjusting device 6 can adjust the amount of refrigerant accumulated in the receiver 5 located on the downstream side, and no refrigerant accumulates in the receiver 6 located on the upstream side. As described above, by operating the plurality of flow rate adjusting devices 6, it is possible to adjust the amount of refrigerant accumulated for each receiver 5, and the amount of circulating refrigerant can be set to an optimum amount according to the operation state.

  A control device 20 for controlling the opening degree of the flow rate adjusting device 6 is provided, and the control device 20 controls the opening degree of at least one flow rate adjusting device 6 to fully open the other flow rate adjusting device 6.

  In the receiver 5 located on the downstream side of the flow rate adjusting device 6 to be controlled, the amount of refrigerant accumulated can be adjusted, and no refrigerant accumulates in the receiver 5 located on the upstream side. Therefore, the receiver 5 in which the refrigerant accumulates is determined according to the flow rate adjustment device 6 to be controlled, and the amount of refrigerant accumulated in all the receivers 5 is changed by controlling the flow rate adjustment device 6 as the control object according to the operation status, and is circulated. The amount of refrigerant to be made can be made the optimum amount of refrigerant.

  At this time, the control device 20 controls the flow control device 6 to be controlled after fully opening the flow control device 6 other than the control target. By arranging the operation order of the flow rate adjusting device 6 as described above, even if the refrigerant is suddenly discharged from the receiver 5 when the refrigerant is accumulated in the receiver 5, the refrigerant is not in the other flow rate adjusting device 6. Pass through smoothly.

  The volume of each receiver 5 is different. The volume of at least one receiver 5 among the plurality of receivers 5 may be different. By selecting the receiver 5 that stores the refrigerant in accordance with the operating conditions, the amount of refrigerant stored in all the receivers 5 can be optimized in accordance with the operating conditions.

  In the air conditioner configured by the indoor unit 10 including the indoor heat exchanger 13 and the outdoor unit 11 including the outdoor heat exchanger 14, the volume of the indoor heat exchanger 13 is larger than the volume of the outdoor heat exchanger 14. When the volume is small, the volume of the receiver 5 near the outdoor heat exchanger 14 is smaller than the volume of the receiver 5 near the indoor heat exchanger 13, and when the volume of the outdoor heat exchanger 14 is smaller than the volume of the indoor heat exchanger 13, The volume of the receiver 5 close to the outdoor heat exchanger 14 is made larger than the volume of the receiver 5 close to the indoor heat exchanger 13. As a result, operation in an excessive refrigerant state can be avoided, and operation with an optimal amount of refrigerant is facilitated.

  The volume of the receiver 5 provided at a position close to the condenser 2 is made smaller than the volume of the other receivers 5. When the refrigerant is stored in the receiver 5 having a small volume, the amount of the circulating refrigerant can be increased. In particular, in the operation mode in which the amount of refrigerant circulating is increased, the refrigerant accumulated in the receiver 5 having a small volume can be quickly adjusted by controlling the flow rate adjusting device 6 on the upstream side of the receiver 5 located near the condenser 2. Therefore, it is possible to easily increase the amount of refrigerant circulating.

  The volume of the receiver 5 located on the upstream side in the refrigerant flow direction is smaller than the volume of the receiver 5 located on the downstream side. That is, the receivers 5 are arranged in ascending order of volume from the upstream side toward the downstream side. Thereby, control of each flow control device 6 for optimizing the amount of circulating refrigerant can be easily performed.

  The receiver 5 includes one inlet / outlet, a connecting pipe 8 branched from the refrigerant circuit is connected to the inlet / outlet of the receiver 5, and the connecting pipe 8 is arranged between the adjacent flow rate adjusting devices 6. Compared to the case where the inlet and outlet of the receiver 5 are separated, only one connecting pipe 8 is required. For this reason, even if there are a plurality of receivers 5, the number of pipes does not increase and the installation space for the receiver 5 can be easily secured.

  The compressor 1, the condenser 2, the throttle unit 3, and the evaporator 4 are provided with a refrigerant circuit that is connected by piping, and the throttle unit 3 adjusts the amount of refrigerant that circulates in the refrigerant circuit and the receiver 5 that stores the refrigerant. The flow rate adjusting device 6 is configured so that the amount of refrigerant circulating in the refrigerant circuit becomes the optimum amount of refrigerant according to the air conditioning operation. When the control device 20 to be controlled is provided and the opening amounts of the plurality of flow rate adjusting devices 6 are equal to or greater than a predetermined opening amount, the control device 20 decreases the rotational speed of the compressor 1. At this time, the control device 20 sets the flow rate adjustment device 6 other than the control target to a predetermined opening degree or more, and then controls the control target flow rate adjustment device 6 to the predetermined opening degree or more.

  When the amount of refrigerant circulating is insufficient, if the flow rate adjusting device 6 is open to the fully open position, it cannot be dealt with any more. However, by reducing the rotation speed of the compressor 1, the opening degree of the flow rate adjusting device 6 is reduced. Changed to Thereby, it becomes possible to control the opening degree of the flow control device 6, and it is possible to eliminate the shortage of refrigerant.

  The compressor 1, the condenser 2, the throttle unit 3, and the evaporator 4 are provided with a refrigerant circuit that is connected by piping, and the throttle unit 3 adjusts the amount of refrigerant that circulates in the refrigerant circuit and the receiver 5 that stores the refrigerant. The flow rate adjusting device 6 is configured so that the amount of refrigerant circulating in the refrigerant circuit becomes the optimum amount of refrigerant according to the air conditioning operation. A control device 20 for controlling is provided, and the control device 20 blows air toward the condenser 2 when the opening degree of the plurality of flow rate adjustment devices 6 is set to a predetermined opening degree or more and the rotational speed of the compressor 1 is reduced. The rotational speed of the fan 15 is lowered.

  When the opening degree of the plurality of flow rate adjusting devices 6 is equal to or greater than a predetermined opening degree, the rotation speed of the compressor 1 is reduced and the rotation speed of the condenser fan 15 is further reduced in order to prevent dew condensation due to insufficient refrigerant. Be lowered. Compared with the case where only the rotation speed of the compressor 1 is lowered, the amount of circulating refrigerant can be increased. The shortage of refrigerant can be quickly resolved and dew can be prevented.

  The compressor 1, the condenser 2, the throttle unit 3, and the evaporator 4 are provided with a refrigerant circuit that is connected by piping, and the throttle unit 3 adjusts the amount of refrigerant that circulates in the refrigerant circuit and the receiver 5 that stores the refrigerant. And a plurality of flow rate adjusting devices 6 for adjusting the amount of refrigerant stored in the receiver 5, and a cooling pipe 30 that cools the receiver 5 by diverting a low-temperature refrigerant from the refrigerant circuit, and a high-temperature refrigerant from the refrigerant circuit. And a heating tube 31 that warms the receiver 5.

  When the receiver 5 is cooled by the low-temperature refrigerant, the refrigerant easily flows into the receiver 5. When the receiver 5 is warmed by the high-temperature refrigerant, the refrigerant is easily discharged from the receiver 5. As a result, the refrigerant smoothly enters and exits the receiver 5.

  A cooling valve 32 that opens and closes the cooling pipe 30 and a heating valve 33 that opens and closes the heating pipe 31 are provided. When the refrigerant is accumulated in the receiver 5, the cooling valve 32 is opened and the heating valve 33 is closed. Is discharged, the cooling valve 32 is closed and the heating valve 33 is opened.

  The control device 20 controls the cooling valve 32 and the heating valve 33 according to the operation status. By controlling the cooling valve 32 and the heating valve 33 in conjunction with the flow rate adjusting device 6, the refrigerant flows in and out of the receiver 5 smoothly, and the amount of circulating refrigerant can be quickly adjusted.

  The heating pipe 31 is connected to a discharge side pipe of the compressor 1, and the cooling pipe 30 is connected to a suction side pipe of the compressor 1. Since the temperature of the refrigerant flowing through the heating pipe 31 is higher than the temperature of the refrigerant in the receiver 5, the liquid refrigerant in the receiver 5 can be evaporated to increase the internal pressure, and the refrigerant is easily discharged. Since the temperature of the refrigerant flowing through the cooling pipe 30 is lower than the temperature of the refrigerant in the receiver 5, the gas refrigerant in the receiver 5 can be liquefied to lower the internal pressure, and the refrigerant easily flows into the receiver 5. Become.

  The cooling pipe 30 and the heating pipe 31 are narrow pipes smaller in diameter than the piping of the refrigerant circuit, and the cooling pipe 30 and the heating pipe 31 are wound around the receiver 5. Although the refrigerant flows from the refrigerant circuit to the cooling pipe 30 or the heating pipe 31, the amount of circulating refrigerant can be reduced only slightly.

  The compressor 1, the condenser 2, the throttle unit 3, and the evaporator 4 are provided with a refrigerant circuit that is connected by piping, and the throttle unit 3 adjusts the amount of refrigerant that circulates in the refrigerant circuit and the receiver 5 that stores the refrigerant. And a plurality of flow rate adjusting devices 6 that adjust the amount of refrigerant stored in the receiver 5, and the receiver 5 includes a plurality of tanks 40.

  Since the small tank 40 can be used, the tank 40 can be arranged in a small gap, and the degree of freedom of arrangement of the receiver 5 is increased. That is, the plurality of tanks 40 are arranged in the gaps in the outdoor unit 11. The gap created in the outdoor unit 11 can be used effectively, and it is possible to reduce the size of the outdoor unit 11 without installing a space for installing the receiver 5.

  A plurality of tanks 40 are connected to one connecting pipe 8 connected to the refrigerant pipe, and the respective tanks 40 are shifted and arranged. Thereby, the refrigerant can be taken in and out in order with respect to each tank 40.

  The compressor 1, the condenser 2, the throttle unit 3, and the evaporator 4 are provided with a refrigerant circuit that is connected by piping, and the throttle unit 3 adjusts the amount of refrigerant that circulates in the refrigerant circuit and the receiver 5 that stores the refrigerant. The flow rate adjusting device 6 is configured so that the amount of refrigerant circulating in the refrigerant circuit becomes the optimum amount of refrigerant according to the air conditioning operation. A control device 20 for controlling is provided, and the control device 20 determines whether or not the refrigeration cycle is stabilized by using a mathematical expression representing a change in the discharge temperature of the compressor 1, and the flow rate adjusting device after the refrigeration cycle is stabilized. The opening degree of 6 is controlled.

  By using the above formula, it is possible to accurately determine the timing at which the refrigeration cycle is stabilized. And since the opening degree of the flow regulating device 6 can be controlled after the refrigeration cycle is reliably stabilized, the amount of circulating refrigerant can be adjusted efficiently.

  A plurality of mathematical formulas using the rotational speed of the compressor 1 as a parameter is prepared, and the control device 20 selects a mathematical formula to be used for determination according to the rotational speed of the compressor 1 during operation. The timing at which the refrigeration cycle is stabilized differs depending on the rotation speed of the compressor 1. Therefore, it is possible to accurately determine that the refrigeration cycle is stable by selecting a mathematical formula corresponding to the rotational speed.

  In addition, this invention is not limited to the said embodiment, Of course, many corrections and changes can be added to the said embodiment within the scope of the present invention. As the flow rate adjusting device 6, a plurality of capillary tubes may be arranged to switch the flow path. Moreover, you may use the expansion valve from which the opening area of a valve differs as the flow volume adjustment apparatus 6. FIG.

  The diameter and length of the connecting pipe 8 connected to the plurality of receivers 5 may be changed. Refrigerant accumulates in each connecting pipe 8, but the amount of accumulated refrigerant is different. Thus, since the connection pipe 8 is also a part of the receiver 5, even if the volume of each receiver 5 is made the same, the volume of each receiver 5 can be varied. When the gap in which the receiver 5 is installed is away from the piping of the refrigerant circuit, the connecting pipe 8 becomes longer and the volume increases accordingly. Even if the volume of the receiver 5 itself is not changed, the volume of the receiver 5 at a far position is different from the volume of other receivers 5 at a near position.

DESCRIPTION OF SYMBOLS 1 Compressor 2 Condenser 3 Restriction part 4 Evaporator 5 Receiver 6 Flow control device 7 Connection pipe 8 Connection pipe 10 Indoor unit 11 Outdoor unit 12 Four-way valve 13 Indoor heat exchanger 14 Outdoor heat exchanger 15 Fan for outdoor heat exchanger DESCRIPTION OF SYMBOLS 16 Fan for indoor heat exchangers 20 Controller 21 Condenser temperature sensor 22 Evaporator temperature sensor 23 Discharge temperature sensor 24 Suction temperature sensor 25 Room temperature sensor 26 Outside temperature sensor 30 Cooling pipe 31 Heating pipe 32 Cooling valve 33 Heating valve 40 Tank 41 Branch pipe

Claims (10)

A compressor, a condenser, a throttle unit, and an evaporator are provided with a refrigerant circuit that is connected by piping. The throttle unit is provided with a plurality of receivers that store the refrigerant and each receiver for adjusting the amount of refrigerant circulating in the refrigerant circuit. It is composed of a plurality of flow rate adjusting devices that adjust the amount of refrigerant to be stored , and each receiver and each flow rate adjusting device are arranged alternately along the flow direction of the refrigerant in the piping connecting the condenser and the evaporator. A featured air conditioner. When the air conditioner is stopped, each flow rate adjusting device is fully opened, and when the air conditioning operation is started , the flow rate adjusting device located downstream of the receiver in the flow direction of the refrigerant operates to The air conditioner according to claim 1, wherein the amount of refrigerant accumulated changes. The control apparatus which controls the opening degree of a flow regulating device is provided, and a control apparatus controls the opening degree of at least 1 flow regulating device, and opens the other flow regulating device fully. 2. The air conditioner according to 2. The volume of each receiver differs, The air conditioner in any one of Claims 1-3 characterized by the above-mentioned. In an air conditioner composed of an indoor unit having an indoor heat exchanger and an outdoor unit having an outdoor heat exchanger, a refrigerant circuit in which a compressor, a condenser, a throttle unit, and an evaporator are connected by piping is provided. The throttle unit includes a plurality of receivers that store refrigerant, and a plurality of flow rate adjustment devices that adjust the amount of refrigerant stored in each receiver in order to adjust the amount of refrigerant circulating in the refrigerant circuit. In contrast, when the volume of the indoor heat exchanger is smaller than the volume of the outdoor heat exchanger, the volume of the receiver near the outdoor heat exchanger is made smaller than the volume of the receiver near the indoor heat exchanger, and the volume of the outdoor heat exchanger is is smaller than the volume of the indoor heat exchanger, air conditioner characterized in that the volume of the receiver near the outdoor heat exchanger is larger than the volume of the receiver near the indoor heat exchanger. A compressor, a condenser, a throttle unit, and an evaporator are provided with a refrigerant circuit that is connected by piping. The throttle unit is provided with a plurality of receivers that store the refrigerant and each receiver for adjusting the amount of refrigerant circulating in the refrigerant circuit. It is composed of a plurality of flow rate adjustment devices that adjust the amount of refrigerant to be stored, a control device that controls the opening degree of the flow rate adjustment device is provided, and when the opening degree of the plurality of flow rate adjustment devices is equal to or greater than a predetermined opening degree, controller, air conditioner you characterized by lowering the rotational speed of the compressor. A compressor, a condenser, a throttle unit, and an evaporator are provided with a refrigerant circuit that is connected by piping. The throttle unit is provided with a plurality of receivers that store the refrigerant and each receiver for adjusting the amount of refrigerant circulating in the refrigerant circuit. And a control device for controlling the opening degree of the flow rate adjusting device. The control device sets the opening amounts of the plurality of flow rate adjusting devices to a predetermined opening degree or more. when lowering the rotational speed of the compressor Te, air conditioner you characterized by lowering the rotational speed of the fan for blowing air toward the condenser. A compressor, a condenser, a throttle unit, and an evaporator are provided with a refrigerant circuit that is connected by piping. The throttle unit is provided with a plurality of receivers that store the refrigerant and each receiver for adjusting the amount of refrigerant circulating in the refrigerant circuit. multiple is composed of a flow control device, air conditioner characterized in that each receiver is constituted of a plurality of tanks for adjusting the amount of refrigerant accumulated. A cooling pipe from the refrigerant circuit by shunting the low-temperature refrigerant for cooling the receiver, one of the claims 1-8, characterized in that the heating pipe is provided to warm the receiver by shunting the high-temperature refrigerant from the refrigerant circuit The air conditioner described in Crab. A control device for controlling the opening degree of the flow rate adjusting device is provided so that the refrigerant amount circulating in the refrigerant circuit becomes an optimum refrigerant amount according to the air conditioning operation, and the control device is a mathematical expression representing a change in the discharge temperature of the compressor. The air conditioning according to any one of claims 1 to 9, wherein it is determined whether or not the refrigeration cycle is stabilized by using and the opening degree of the flow rate adjusting device is controlled after the refrigeration cycle is stabilized. Machine.

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