JP6479162B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner that minimizes the amount of refrigerant leakage.

  In current air conditioners such as multi air conditioners for buildings, the total length of refrigerant piping connecting an outdoor unit and multiple indoor units may be several hundred meters, and the amount of refrigerant used is very large. Become. In such an air conditioner, a large amount of refrigerant may leak into one room when refrigerant leakage occurs.

  In recent years, from the viewpoint of global warming, conversion to a refrigerant having a low global warming potential is required, but many refrigerants having a low global warming potential are flammable. In the future, when the transition to refrigerants with a low global warming potential progresses, further consideration for safety will be required. In order to solve such a problem, a technology has been proposed in which a shut-off valve for closing the flow of the refrigerant is provided in the refrigerant circuit to reduce the amount of refrigerant leaked when the refrigerant leaks (for example, a patent) Reference 1).

JP 2000-97527 A (FIG. 1 etc.)

  However, the technique described in Patent Document 1 can reduce the amount of refrigerant leakage when the refrigerant leaks, but the position of a shut-off valve for closing the refrigerant flow and refrigerant leakage occur. Depending on the location, there is a problem that many refrigerants leak.

  The present invention has been made to solve the above-described problems, and is an air conditioner that reduces the amount of refrigerant leakage when refrigerant leakage occurs regardless of the operation mode such as cooling operation or heating operation. The purpose is to obtain.

An air conditioner according to the present invention, a compressor, a flow path switching unit, a first heat exchanger, a diaphragm Ri device, a second heat exchanger is formed by connecting the accumulator by a pipe Cooling operation in which the first heat exchanger acts as a condenser and the second heat exchanger acts as an evaporator by switching the flow path switching device, and the second heat exchanger is a condenser In the air conditioner that can be switched to any one of the heating operation in which the first heat exchanger acts as an evaporator, the first provided in the pipe between the first heat exchanger and the expansion device The flow path switching device is oriented in the cooling operation so that the refrigerant in the pipe is recovered by the first heat exchanger and the accumulator when the leakage of the switching device and the refrigerant is detected , and the first It performs a pump-down operation for controlling the opening and closing device and the compressor, then recovered As refrigerant is enclosed in the first heat exchanger and the accumulator, the flow path switching unit and the direction of the heating operation, and the refrigerant leakage amount for controlling the compressor and the expansion device and the first switching device And a control device that performs a reducing operation, and the control device fully closes the expansion device when performing the refrigerant leakage amount reducing operation .

  According to the present invention, when leakage of the refrigerant is detected, the refrigerant in the refrigerant circuit is collected in the first heat exchanger and the accumulator, and then the collected refrigerant is enclosed in the first heat exchanger and the accumulator. As a result, the amount of refrigerant leaked into the indoor space can be reduced.

The refrigerant circuit figure which shows an example of schematic structure of the air conditioning apparatus which concerns on Embodiment 1 of this invention. The refrigerant circuit figure which shows the flow of the refrigerant | coolant at the time of the cooling operation mode of the air conditioning apparatus of FIG. The refrigerant circuit figure which shows the flow of the refrigerant | coolant at the time of the heating operation mode of the air conditioning apparatus of FIG. The flowchart which shows the operation | movement of the refrigerant | coolant leak prevention control in the air conditioning apparatus of FIG. The flowchart which shows the pump down operation | movement in the air_conditioning | cooling operation mode of the air conditioning apparatus of FIG. The flowchart which shows the refrigerant | coolant leakage amount reduction operation | movement at the time of the air_conditioning | cooling operation mode of the air conditioning apparatus of FIG. The flowchart which shows the pump down operation in the heating operation mode of the air conditioning apparatus of FIG. 3, and the pump down operation in the stop mode. The refrigerant circuit figure which shows an example of schematic structure of the air conditioning apparatus which concerns on Embodiment 2 of this invention. The refrigerant circuit figure which shows the flow of the refrigerant | coolant at the time of the air_conditioning | cooling operation mode of the air conditioning apparatus of FIG. The refrigerant circuit figure which shows an example of schematic structure of the air conditioning apparatus which concerns on Embodiment 3 of this invention.

  Hereinafter, embodiments of an air-conditioning apparatus according to the present invention will be described with reference to the drawings. In addition, the form of drawing is an example and does not limit this invention. Moreover, what attached | subjected the same code | symbol in each figure is the same or it corresponds, and this is common in the whole text of a specification. Furthermore, in the following drawings, the relationship between the sizes of the constituent members may be different from the actual one.

Embodiment 1 FIG.
1 is a refrigerant circuit diagram illustrating an example of a schematic configuration of an air-conditioning apparatus according to Embodiment 1 of the present invention.
In FIG. 1, an air conditioner 100 includes, for example, a building including a refrigerant circuit including an outdoor unit 1 and two indoor units 2 a and 2 b connected to the outdoor unit 1 via a refrigerant main pipe 3. Multi air conditioner. The air conditioner 100 circulates refrigerant in a refrigerant circuit and performs air conditioning using a refrigeration cycle. The air conditioner 100 is a cooling only operation mode in which all indoor units 2a and 2b perform cooling, and all indoor units 2a and 2b. It is the structure which can select arbitrarily the all-heating operation mode which heats.

[Outdoor unit 1]
The outdoor unit 1 includes a compressor 10, a flow path switching device 11 including a four-way valve, a heat source side heat exchanger 12, a refrigerant shut-off device 13, and an accumulator 14, each of which is a refrigerant pipe. 4 are connected. In addition, an outdoor blower 16 that blows air to the heat source side heat exchanger 12 is provided in the vicinity of the heat source side heat exchanger 12. The heat source side heat exchanger 12 corresponds to the “first heat exchanger” in the present invention, the outdoor blower 16 corresponds to the “blower” in the present invention, and the refrigerant shut-off device 13 in the present invention “ It corresponds to a “first opening / closing device”.

  The compressor 10 sucks a low-temperature and low-pressure gas refrigerant and compresses the gas refrigerant to a high-temperature and high-pressure state. For example, the compressor 10 includes an inverter compressor that can control the capacity. The flow path switching device 11 switches the refrigerant flow in the cooling operation mode and the refrigerant flow in the heating operation mode.

  The heat source side heat exchanger 12 acts as a condenser during the cooling operation, acts as an evaporator during the heating operation, and performs heat exchange between the air supplied from the outdoor blower 16 and the refrigerant. The refrigerant shut-off device 13 is configured by, for example, an electromagnetic valve that blocks the flow of the refrigerant circulating in the refrigerant pipe 4. In addition, although the solenoid valve is used for the refrigerant | coolant interruption | blocking apparatus 13, as long as it can interrupt | block the flow of a refrigerant | coolant, anything may be used.

  The outdoor unit 1 branches from the refrigerant pipe 4 on the refrigerant shut-off device 13 side connected to one refrigerant main pipe 3 and is connected to the refrigerant pipe 4 connecting the flow path switching device 11 and the suction side of the compressor 10. The bypass pipe 5 and a bypass switch 15 installed in the middle of the bypass pipe 5 are provided. The bypass opening / closing device 15 corresponds to the “second opening / closing device” in the present invention, and is configured by, for example, an electromagnetic valve that blocks the flow of the refrigerant in the bypass pipe 5. In addition, in FIG. 1, although the connection location of the bypass piping 5 has shown the example which exists in the inside of the outdoor unit 1, it is not restricted to this. Moreover, although the electromagnetic valve is used for the bypass opening / closing device 15, anything may be used as long as it can block the flow of the refrigerant.

  Further, the outdoor unit 1 is provided with a first pressure detection device 20 and a second pressure detection device 21. The first pressure detection device 20 is installed in the refrigerant pipe 4 connecting the discharge side of the compressor 10 and the flow path switching device 11, and detects the pressure P1 of the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 10. To do. The second pressure detection device 21 is installed in the refrigerant pipe 4 connecting the flow path switching device 11 and the suction side of the compressor 10 and detects the pressure P2 of the low-temperature and low-pressure gas refrigerant sucked into the compressor 10. To do.

  Further, the outdoor unit 1 is provided with a first temperature detection device 22 configured by, for example, a thermistor. The first temperature detection device 22 is installed in the refrigerant pipe 4 that connects the discharge side of the compressor 10 and the flow path switching device 11, and detects the temperature of the high-temperature and high-pressure gas refrigerant that is compressed and discharged by the compressor 10. .

[Indoor units 2a, 2b]
The indoor units 2a and 2b include load-side heat exchangers 40a and 40b, expansion devices 41a and 41b, and indoor blowers 42a and 42b, respectively. These indoor units 2a and 2b are connected to the outdoor unit 1 via the refrigerant main pipe 3, so that the refrigerant flows in and out. The load-side heat exchangers 40a and 40b exchange heat between the air supplied from the indoor fans 42a and 42b and the refrigerant, and generate heating air or cooling air supplied to the indoor space. In addition, the expansion devices 41a and 41b are configured by electronic expansion valves having functions as pressure reducing valves and expansion valves, for example. The load-side heat exchangers 40a and 40b correspond to the “second heat exchanger” in the present invention.

  In the indoor units 2a and 2b, second temperature detection devices 50a and 50b are installed in a refrigerant pipe connecting the load side heat exchangers 40a and 40b and the expansion devices 41a and 41b. In addition, third temperature detection devices 51a and 51b are installed in the refrigerant pipes of the load side heat exchangers 40a and 40b opposite to the expansion devices 41a and 41b. Further, fourth temperature detection devices 52a and 52b are arranged on the air suction side of the load side heat exchangers 40a and 40b.

  The second temperature detection devices 50a and 50b detect the temperature of the refrigerant flowing into the load side heat exchangers 40a and 40b during the cooling operation. Moreover, the 3rd temperature detection apparatuses 51a and 51b detect the temperature of the refrigerant | coolant which flows out out of load side heat exchanger 40a, 40b. Furthermore, the fourth temperature detection devices 52a and 52b detect the indoor air temperature. For example, a thermistor is used in each of the temperature detection devices described above.

  The air conditioner 100 has a control device 30 configured by a microcomputer or the like. When the control device 30 detects a refrigerant leak from detection values of gas sensors installed in the room or various measurement sensors installed in the indoor units 2a and 2b, the refrigerant in the refrigerant circuit and the heat source side heat exchanger 12 are exchanged. In order to be collected by the accumulator 14, the flow path switching device is set in the direction during the cooling operation, and the pump-down operation for controlling the refrigerant shut-off device 13, the bypass opening / closing device 15, and the compressor 10 is performed. Thereafter, the control device 30 sets the flow path switching device 11 in the heating operation direction so that the recovered refrigerant is contained in the heat source side heat exchanger 12 and the accumulator 14, and the refrigerant shut-off device 13 and the bypass switch 15 The refrigerant leakage amount reducing operation for controlling the compressor 10 and the compressor 10 is performed.

  Furthermore, the control device 30 switches the operation frequency of the compressor 10, the rotational speed of the outdoor fan 16 (including ON / OFF), and the flow path switching device 11 based on the detection values from various detection devices and instructions from the remote controller. Then, the opening degree of the expansion devices 41a and 41b is controlled, and each operation mode described later is executed. Although FIG. 1 shows an example in which the control device 30 is provided in the outdoor unit 1, it may be provided separately for each unit of the outdoor unit 1 or the indoor units 2a and 2b. You may provide in either 2a, 2b.

[Cooling operation mode]
In the air conditioning apparatus 100 configured as described above, a cooling operation mode when a cooling load is generated in the load-side heat exchangers 40a and 40b will be described with reference to FIG.
FIG. 2 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus of FIG. 1 is in the cooling operation mode. In addition, the solid line arrow shown in the figure has shown the flow direction of the refrigerant | coolant.

  In the cooling operation mode, the low-temperature and low-pressure gas refrigerant sucked into the compressor 10 is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the flow path switching device 11. The high-temperature and high-pressure gas refrigerant that has flowed into the heat source side heat exchanger 12 is condensed while dissipating heat to the outdoor air, and becomes high-pressure liquid refrigerant. Then, the high-pressure liquid refrigerant that has flowed out of the heat source side heat exchanger 12 passes through the open refrigerant blocking device 13 and flows out of the outdoor unit 1, passes through the refrigerant main pipe 3, and enters the indoor units 2 a and 2 b. Inflow. At this time, the bypass opening / closing device 15 is closed to prevent the refrigerant from bypassing in the outdoor unit 1.

  The refrigerant shut-off device 13 in the cooling operation mode is opened when the device cannot adjust the opening, such as a solenoid valve, and when the device can adjust the opening (opening area), such as an electronic expansion valve. The opening (for example, fully open) is set such that the operating state (for example, cooling capacity) of the refrigeration cycle is not adversely affected.

  Further, the bypass opening / closing device 15 in the cooling operation mode is opened when the opening degree cannot be adjusted, such as a solenoid valve, and when the opening degree is adjustable, such as an electronic expansion valve, The opening (for example, fully open) is set such that the operation state (for example, cooling capacity) of the cycle is not adversely affected.

  The high-pressure liquid refrigerant that has flowed into the indoor unit 2 is decompressed to a low-temperature and low-pressure gas-liquid two-phase refrigerant by the expansion device 41, and then flows into the load-side heat exchanger 40 that functions as an evaporator, and absorbs heat from the indoor air. As a result, the indoor air is cooled to become a low-temperature and low-pressure gas refrigerant. The low-temperature and low-pressure gas refrigerant flowing out from the load-side heat exchanger 40 flows into the outdoor unit 1 through the refrigerant main pipe 3. The low-temperature and low-pressure gas refrigerant flowing into the outdoor unit 1 passes through the flow path switching device 11 and the accumulator 14 and is sucked into the compressor 10.

  The expansion devices 41a and 41b have a constant superheat (degree of superheat) obtained as a difference between the temperature detected by the second temperature detection devices 50a and 50b and the temperature detected by the third temperature detection device 51. Thus, the opening degree is controlled by the control device 30.

[Heating operation mode]
Next, the heating operation mode in the case where a thermal load is generated in the load-side heat exchanger 40 will be described with reference to FIG.
FIG. 3 is a refrigerant circuit diagram illustrating a refrigerant flow when the air-conditioning apparatus of FIG. 1 is in the heating operation mode. In addition, the solid line arrow shown in the figure has shown the flow direction of the refrigerant | coolant.

  In the heating operation mode shown in FIG. 3, the low-temperature and low-pressure gas refrigerant sucked into the compressor 10 is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the indoor unit 2 through the refrigerant main pipe 3 via the flow path switching device 11. The high-temperature and high-pressure gas refrigerant that has flowed into the indoor unit 2 radiates heat to the indoor air in the load-side heat exchanger 40 and flows into the expansion device 41 as high-pressure liquid refrigerant. Then, after the pressure is reduced to a low-temperature and low-pressure gas-liquid two-phase refrigerant by the expansion device 41, the refrigerant flows out of the indoor unit 2 and flows into the outdoor unit 1 through the refrigerant main pipe 3.

  The low-temperature and low-pressure two-phase refrigerant that has flowed into the outdoor unit 1 passes through the open refrigerant blocking device 13 and absorbs heat from the outdoor air in the heat source side heat exchanger 12 to become a low-temperature and low-pressure gas refrigerant. The low-temperature and low-pressure gas refrigerant flowing out of the heat source side heat exchanger 12 passes through the flow path switching device 11 and the accumulator 14 and is sucked into the compressor 10.

  The refrigerant shut-off device 13 in the heating operation mode is opened when the device cannot adjust the opening, such as an electromagnetic valve, and operates in the refrigeration cycle when the device can adjust the opening, such as an electronic expansion valve. The opening (for example, fully open) is set such that the state (for example, heating capacity) is not adversely affected.

  Further, the bypass opening / closing device 15 in the heating operation mode is opened when the opening degree of the device such as a solenoid valve cannot be adjusted, and is refrigeration cycle when the opening degree can be adjusted such as an electronic expansion valve. The opening degree (for example, fully open) is set such that the operation state (for example, heating capacity) is not adversely affected.

  The expansion devices 41a and 41b are obtained as a difference between the refrigerant saturated liquid temperature calculated from the pressure detected by the first pressure detection device 20 and the temperature detected by the second temperature detection devices 50a and 50b. The opening degree is controlled by the control device 30 so that the subcool (degree of supercooling) is constant.

Next, refrigerant leakage prevention control will be described.
As described above, the refrigerant leakage prevention control is one of the functions of the control device 30, and the refrigerant leakage is detected from the detection values of the gas sensors installed in the room or the various measurement sensors installed in the indoor units 2a and 2b. This is a control function that is started upon detection. Moreover, although the specific example which detects generation | occurrence | production of refrigerant | coolant leakage was described, it is not restricted to this, What kind of method may be used if the generation | occurrence | production of refrigerant | coolant leakage can be detected and it becomes the starting point of control operation | movement. .

FIG. 4 is a flowchart showing the operation of refrigerant leakage prevention control in the air conditioning apparatus of FIG.
When detecting the occurrence of refrigerant leakage (S1), control device 30 starts refrigerant leakage prevention control. That is, the control device 30 performs a pump-down operation that causes the outdoor unit 1 to recover the liquid refrigerant on the indoor unit 2 side (S2). Thereafter, the control device 30 performs a refrigerant leakage amount reducing operation for preventing the liquid refrigerant collected in the outdoor unit 1 from returning to the indoor unit 2 (S3).

[Refrigerant leakage prevention control during cooling operation mode]
The pump-down operation of the refrigerant leakage prevention control in the cooling operation mode will be described in detail with reference to FIG.
FIG. 5 is a flowchart showing a pump-down operation in the cooling operation mode of the air-conditioning apparatus of FIG.
First, the control device 30 maintains the flow channel in the cooling operation mode in the flow channel switching device 11 (S11), and then sets the operating frequency of the compressor 10 to a predetermined value (S12). Then, the control device 30 closes the refrigerant shut-off device 13 and opens the bypass opening / closing device 15 (S13, S14). Further, the control device 30 sets the rotational speed of the outdoor blower 16 to a predetermined value (S15), and finally the pressure P1 detected by either the first pressure detection device 20 or the second pressure detection device 21. When (or P2) reaches the threshold value, the pump-down operation is terminated (S16).

  If the predetermined value of the operating frequency of the compressor 10 set in S12 is set to a high frequency, the pressure of the refrigeration cycle changes abruptly and there is a risk of an abnormal stop or the like. On the other hand, if the frequency is low, the pump-down effect is reduced. Therefore, it is not preferable to rotate at the lowest operating frequency allowed by the compressor 10. For this reason, it is preferable to perform the pump-down operation at an operating frequency that is half the lowest frequency and the highest frequency.

  The predetermined value of the rotational speed of the outdoor blower 16 set in S15 may be set to the maximum rotational speed. By setting the rotational speed of the outdoor blower 16 to the maximum rotational speed, the refrigerant is likely to condense in the heat source side heat exchanger 12, and the discharge pressure of the compressor 10 can be prevented from increasing.

  When the threshold value for ending the pump-down operation set in S16 is set as high as possible on the high-pressure side and as low as possible on the low-pressure side, a large amount of refrigerant is discharged from the indoor unit 2 to the outdoor. It can be moved to the machine 1 and safer. For this reason, in the case of the 1st pressure detection apparatus 20, it is good to set it as the value (1st threshold value) close | similar to the maximum pressure which the compressor 10 accept | permits at the time of operation | movement, or the maximum pressure. In the case of the second pressure detection device 21, it is preferable to set the minimum pressure allowed by the compressor 10 during operation or a value close to the minimum pressure (second threshold). In S16 of FIG. 5, the pump-down operation is terminated when either one of the first pressure detection device 20 or the second pressure detection device 21 reaches the threshold value. When the detected pressure (P1) of the first pressure detection device 20 is equal to or higher than the first threshold value and the detected pressure (P2) of the second pressure detection device 21 is equal to or lower than the second threshold value, the pump down operation is performed. You may make it complete | finish.

  By performing the pump-down operation shown in FIG. 5 during the cooling operation mode, the refrigerant in the refrigerant pipe 4 that connects the expansion device 41 to the heat source side heat exchanger 12 in which a large amount of liquid refrigerant exists in the cooling operation mode is bypassed 5 The heat source side heat exchanger 12 and the accumulator 14 can be recovered via the. For this reason, the quantity of the liquid refrigerant of the refrigerant | coolant which exists in the indoor unit 2 and the refrigerant | coolant main pipe 3 to connect decreases, and the refrigerant | coolant amount which leaks to indoor space can be reduced.

  In addition, although the specific operation | movement order of pump down operation | movement is described in FIG. 5, it is not limited to this, About S11-S15, the same effect can be acquired even if an operation | movement order is reversed. it can.

FIG. 6 is a flowchart showing the refrigerant leakage amount reducing operation in the cooling operation mode of the air conditioner of FIG.
The control device 30 first switches the flow path switching device 11 to the flow path in the heating operation mode (S21), and then keeps the refrigerant shut-off device 13 closed (S22). Then, the control device 30 closes the bypass opening / closing device 15 (S23) and stops the operation of the compressor 10 (S24). Further, the control device 30 stops the outdoor blower 16 (S25), and finally closes the expansion device 41 (S26).

  By performing the refrigerant leakage amount reducing operation shown in FIG. 6, the refrigerant recovered by the heat source side heat exchanger 12 and the accumulator 14 can be enclosed in the outdoor unit 1, and movement to the indoor unit 2 can be prevented. For this reason, the amount of refrigerant leaking into the indoor space can be reduced, and safety is improved.

  Moreover, since the upstream side and the downstream side of the expansion device 41 are divided by fully closing the expansion device 41, the amount of refrigerant that leaks can be further reduced, and safety is improved.

  Although FIG. 6 shows a specific operation sequence of the refrigerant leakage amount reducing operation, the present invention is not limited to this, and the same effect can be obtained even if the operation sequence is reversed.

[Refrigerant leakage prevention control in heating operation mode]
The refrigerant leakage prevention control in the heating operation mode will be described in detail.
FIG. 7 is a flowchart showing a pump-down operation in the heating operation mode and a pump-down operation in the stop mode of the air-conditioning apparatus of FIG.
The control device 30 first switches the flow channel switching device 11 to the flow channel in the cooling operation mode (S31), and then sets the operating frequency of the compressor 10 to a predetermined value (S32). Then, the control device 30 closes the refrigerant shut-off device 13 (S33) and opens the bypass opening / closing device 15 (S34). Further, the control device 30 sets the rotational speed of the outdoor blower 16 to a predetermined value (S35), and finally the pressure P1 detected by either the first pressure detection device 20 or the second pressure detection device 21. When (or P2) reaches the threshold value, the pump-down operation is terminated (S36).

  The pump down operation of the refrigerant leakage prevention control in the heating operation mode is the same operation except that the switching operation of the flow path switching device 11 shown in the first S11 of the pump down operation in the cooling operation mode is different. is there.

  By performing the pump-down operation shown in FIG. 7 in the heating operation mode, the refrigerant main pipe that connects the load-side heat exchanger 40 in which a large amount of liquid refrigerant exists in the heating operation mode and the refrigerant shut-off device 13 from the load-side heat exchanger 40 3 can be recovered by the heat source side heat exchanger 12 and the accumulator 14. For this reason, the quantity of the liquid refrigerant | coolant of the refrigerant | coolant which exists in the indoor unit 2 and the refrigerant | coolant main pipe 3 decreases, and the refrigerant | coolant amount which leaks to indoor space can be reduced.

  Further, FIG. 7 shows a specific operation sequence of the pump-down operation, but the present invention is not limited to this. For S31 to S35, the same effect can be obtained even if the operation sequence is reversed. it can.

  The refrigerant leakage amount reduction operation in the heating operation mode is the same as the refrigerant leakage amount reduction operation in the cooling operation mode shown in FIG. For this reason, the refrigerant | coolant collect | recovered by the heat source side heat exchanger 12 and the accumulator 14 can be enclosed in the outdoor unit 1, and the movement to the indoor unit 2 can be prevented. Thereby, the refrigerant | coolant amount leaked to indoor space can be restrained small, and safety | security improves.

  Moreover, since the upstream side and the downstream side of the expansion device 41 are divided by fully closing the expansion device 41, the amount of refrigerant that leaks can be further reduced, and safety is improved.

[Refrigerant leakage prevention control in stop mode]
The refrigerant leakage prevention control when the refrigerant leaks when the air conditioner 100 is stopped (hereinafter referred to as the stop mode) will be described.
The pump-down operation of the refrigerant leakage prevention control performed when refrigerant leakage occurs in the stop mode is the same as the pump-down operation in the heating operation mode shown in FIG. 7, and the same effect can be obtained. However, since the compressor 10 is not moving in the stop mode and the pressure in the refrigerant circuit is constant, the operation of the device driven using the differential pressure is performed by setting the operating frequency of the compressor 10 to a predetermined value. It is necessary to carry out after generating a pressure difference inside.

  In the stop mode, where the liquid refrigerant is present in the air-conditioning apparatus 100 is affected by the indoor and outdoor temperature conditions, the elapsed time since the stop, and the like, the location where the liquid refrigerant is present changes from time to time. . By performing the pump-down operation shown in FIG. 7, the ratio of the liquid refrigerant contained in the indoor unit 2 and the refrigerant main pipe 3 can be reduced, and the amount of refrigerant leaking into the indoor space can be reduced.

  The refrigerant leakage amount reducing operation of the refrigerant leakage prevention control in the stop mode is the same as the refrigerant leakage amount reducing operation in the cooling operation mode shown in FIG. 6, and the same effect can be obtained.

[Refrigerant leakage prevention control during thermo-off mode]
The refrigerant leakage prevention control when refrigerant leakage occurs when the air conditioner 100 is thermo-off (hereinafter referred to as the thermo-off mode) will be described.
The pump-down operation of the refrigerant leak prevention control performed when the refrigerant leak occurs in the thermo-off mode is the same as the pump-down operation in the heating operation mode shown in FIG. 7, and the same effect can be obtained. However, since the compressor 10 is not moving in the thermo-off mode and the pressure in the refrigerant circuit is constant, the operation of the device driven using the differential pressure is performed by setting the operating frequency of the compressor 10 to a predetermined value. This must be done after creating a pressure differential in the circuit.

  The refrigerant leakage amount reduction operation of the refrigerant leakage prevention control in the thermo-off mode is the same as the refrigerant leakage amount reduction operation in the cooling operation mode shown in FIG. 6, and the same effect can be obtained.

  In the first embodiment, an example is shown in which two indoor units 2 are connected to the outdoor unit 1 via the refrigerant main pipe 3, but the number of indoor units 2 connected is limited to two. However, one or three or more indoor units 2 may be connected to the outdoor unit 1.

Embodiment 2. FIG.
In the second embodiment of the present invention, only the parts different from the first embodiment will be described.
FIG. 8 is a refrigerant circuit diagram illustrating an example of a schematic configuration of the air-conditioning apparatus according to Embodiment 2 of the present invention.
The difference between the second embodiment and the first embodiment is that an internal heat exchanger 17 is provided on the refrigerant pipe 4 on which the refrigerant shut-off device 13 is installed, and the flow dividing portion of the bypass pipe 5 is connected to the internal heat exchanger 17. The refrigerant branch 4 is branched from the refrigerant pipe 4 between the first and second expansion devices 41, and the bypass switch 15 is installed in the bypass pipe 5 between the branch point and the internal heat exchanger 17.

  In the second embodiment, since the internal heat exchanger 17 is used, a part of the high-pressure liquid refrigerant generated by the heat source side heat exchanger 12 mainly in the cooling operation mode is bypassed by the bypass pipe 5 to bypass By depressurizing the generated refrigerant, a low-pressure and low-temperature gas-liquid two-phase refrigerant is produced, and heat exchange is performed inside the internal heat exchanger 17, whereby the degree of supercooling of the refrigerant flowing through the refrigerant main pipe 3 can be increased. As the bypass opening / closing device 15, a variable opening degree, for example, an electronic expansion valve is used. Thereby, the exit supercooling degree of the internal heat exchanger 17 can be controlled.

FIG. 9 is a refrigerant circuit diagram showing a refrigerant flow when the air-conditioning apparatus of FIG. 8 is in the cooling operation mode. In addition, the solid line arrow shown in the figure has shown the flow direction of the refrigerant | coolant.
The difference from the first embodiment is that the bypass opening / closing device 15 is in an open state, so that in the cooling operation mode, the refrigerant is bypassed from the upstream side of the expansion device 41, and the bypass opening / closing device 15 and the internal heat exchanger are bypassed. This is the point that a flow that passes through 17 is added.

  Since the refrigerant flow in the heating operation mode is the same as that in the first embodiment, the description thereof is omitted.

[Refrigerant Leakage Prevention Control of Embodiment 2]
The refrigerant leakage prevention control according to the second embodiment can obtain the same effect by making the operation in each operation mode described in the first embodiment the same. Therefore, the description is omitted.

  In the first embodiment, in order to perform the pump-down operation of the refrigerant leakage prevention control, it is necessary to provide the bypass pipe 5 and the bypass switch 15 that are not used in the normal cooling operation mode and heating operation mode. However, in the second embodiment, the bypass pipe 5 and the bypass opening / closing device 15 are required to make the internal heat exchanger 17 that increases the degree of supercooling of the refrigerant flowing into the indoor unit 2 function in the cooling operation mode. . For this reason, it is not necessary to increase a component only for the pump down operation | movement of refrigerant | coolant leakage prevention control.

Embodiment 3 FIG.
For the third embodiment of the present invention, only the parts different from the first embodiment will be described. The air-conditioning apparatus 100 according to Embodiment 3 has a configuration in which the outdoor unit 1 and the heat medium conversion device 60 are connected by the refrigerant main pipe 3, and the heat medium conversion device 60 and the indoor unit 2 are connected by the heat medium pipe 64. It has become.

[Outdoor unit 1]
Since the outdoor unit 1 according to the third embodiment has the same configuration as that of the first embodiment, the description thereof is omitted.

[Indoor unit 2]
The indoor unit 2 according to the third embodiment has the same configuration as that of the first embodiment except that the pipe connecting each component is changed from the refrigerant pipe 4 to the heat medium pipe 64, and thus the description thereof is omitted.

[Heat medium conversion device 60]
The heat medium conversion device 60 includes a heat medium heat exchanger 61, a pump 62 that conveys a heat medium such as water or brine, and a flow rate adjustment device 63 that adjusts the flow rate of the heat medium flowing in the heat medium pipe 64. It is configured to be connected to the heat medium pipe 64 and is installed in a space such as a machine room or a ceiling.

  The heat medium heat exchanger 61 exchanges heat between the refrigerant supplied from the outdoor unit 1 and the heat medium, and includes, for example, a plate heat exchanger. Using the heat exchanged from the refrigerant to the heat medium by the heat medium heat exchanger 61, the indoor unit 2 can perform a cooling operation or a heating operation.

  The flow rate adjusting device 63 is for adjusting the flow rate of the heat medium supplied to the indoor unit 2, and has a mechanism capable of arbitrarily adjusting the opening degree. Further, when the flow rate adjustment device 63 is controlled so that the temperature difference between the third temperature detection device 51 and the fourth temperature detection device 52 installed in the indoor unit 2 is constant, the capacity is increased according to the indoor load. It is convenient because it is adjusted.

  In the third embodiment, an example is shown in which one heat medium conversion device 60 and one indoor unit 2 are provided. However, the present invention is not limited to this, and there are a plurality of heat medium conversion devices 60 and a plurality of indoor units 2. A stand may be connected.

[Refrigerant Leakage Prevention Control of Embodiment 3]
The refrigerant leakage prevention control according to the third embodiment can obtain the same effect by making the operation in each operation mode described in the first embodiment the same. Therefore, the description is omitted.

  Even in the indirect air conditioning system in which the refrigerant does not flow to the indoor unit 2 as in the third embodiment, by performing the refrigerant leakage prevention control, it is possible to reduce the amount of refrigerant leakage to the machine room, the ceiling, etc. The air conditioner 100 can be made.

  In the first to third embodiments, an example in which the bypass pipe 5 and the bypass opening / closing device 15 are provided in the outdoor unit 1 is shown. good. In this case, the same effect can be obtained.

  In the first to third embodiments, the case where there is one outdoor unit 1 has been described as an example. However, the number of the outdoor units 1 is not limited to one, and a plurality of cases when a refrigerant leak occurs. Each of the outdoor units 1 may perform the refrigerant leakage prevention control defined in each embodiment, and the same effect can be obtained.

  In a system in which a plurality of indoor units 2 are connected, not only a system in which all connected indoor units 2 perform cooling or heating operation, but also a system in which cooling operation and heating operation are performed simultaneously according to the indoor unit 2 may be used.

  In this case, when the heat source side heat exchanger 12 of the outdoor unit 1 acts as a condenser, the refrigerant leakage prevention control in the cooling operation mode is performed, and the heat source side heat exchanger 12 of the outdoor unit 1 evaporates. When acting as a heater, the same effect can be obtained by performing refrigerant leakage prevention control in the heating operation mode.

  Further, in the first to third embodiments, the case where one compressor 10 is connected to the outdoor unit 1 has been described as an example, but the outdoor unit in which two or more compressors 10 are connected is described. 1 may be sufficient.

  In the first to third embodiments, the example in which the refrigerant shut-off device 13 is provided in the outdoor unit 1 has been described. However, the present invention is not limited to this, and it is between the heat source side heat exchanger 12 and the expansion device 41. Good anywhere.

  DESCRIPTION OF SYMBOLS 1 Outdoor unit, 2 (2a, 2b) Indoor unit, 3 Refrigerant main pipe, 4 Refrigerant pipe, 5 Bypass pipe, 10 Compressor, 11 Flow path switching device, 12 Heat source side heat exchanger, 13 Refrigerant shut-off device, 14 Accumulator, DESCRIPTION OF SYMBOLS 15 Bypass switchgear, 16 Outdoor fan, 17 Internal heat exchanger, 20 1st pressure detection apparatus, 21 2nd pressure detection apparatus, 22 1st temperature detection apparatus, 30 Control apparatus, 40 (40a, 40b) Load Side heat exchanger, 41 (41a, 41b) throttle device, 42 (42a, 42b) indoor blower, 50 (50a, 50b) second temperature detection device, 51 (51a, 51b) third temperature detection device, 52 (52a, 52b) Fourth temperature detection device, 60 heat medium conversion device, 61 heat medium heat exchanger, 62 pump, 63 flow rate adjustment device, 64 heat medium piping, 100 empty Air conditioning equipment.

Claims (15)

Comprising a compressor, a flow path switching unit, a first heat exchanger, a device for the aperture, a second heat exchanger, a refrigerant circuit which is formed and an accumulator connected by piping, the flow path By switching the switching device, the first heat exchanger serves as a condenser and the second heat exchanger serves as an evaporator, and the second heat exchanger serves as a condenser and the first heat exchanger serves as a condenser. In an air conditioner that can be switched to any one of heating operation in which the heat exchanger of the above acts as an evaporator,
A first switchgear provided in a pipe between the first heat exchanger and the expansion device;
When the leakage of the refrigerant is detected, the flow path switching device is oriented in the cooling operation so that the refrigerant in the pipe is recovered by the first heat exchanger and the accumulator , and the first A pump-down operation for controlling the opening / closing device 1 and the compressor is performed, and then the flow path switching device is heated during the heating operation so that the recovered refrigerant is contained in the first heat exchanger and the accumulator. And a controller for performing a refrigerant leakage amount reducing operation for controlling the first opening / closing device, the compressor, and the expansion device ,
The control device is an air conditioner that fully closes the expansion device when performing the refrigerant leakage amount reducing operation . Wherein the control device, when performing the pump-down operation, said first switching device is closed, the air conditioner according to claim 1 for controlling the operation frequency of the compressor. Wherein the control device, when performing refrigerant leakage amount reducing operation, said first switching device is closed, the air conditioning apparatus according to claim 1 or 2, wherein to stop the operation of the compressor. A bypass pipe branched from a pipe between the first opening and closing device and the expansion device, and connected to a pipe between the flow path switching device and the accumulator;
The air conditioner according to claim 1, further comprising a second opening / closing device installed on the bypass pipe. The air conditioner according to claim 4 , wherein the control device controls the first and second opening / closing devices and the compressor when performing a pump-down operation or a refrigerant leakage amount reducing operation. The air conditioner according to claim 5 , wherein when the pump down operation is performed, the control device closes the first opening / closing device, opens the second opening / closing device, and controls an operating frequency of the compressor. The air according to claim 5 or 6 , wherein when the refrigerant leakage amount reducing operation is performed, the control device closes the first opening and closing device, closes the second opening and closing device, and stops the operation of the compressor. Harmony device. The first heat exchanger is provided with a blower for blowing outside air,
The air conditioner according to any one of claims 1 to 7 , wherein the control device maximizes the rotational speed of the blower while performing a pump-down operation. A first pressure detection device for detecting the pressure on the discharge side of the compressor;
A second pressure detection device for detecting the pressure on the suction side of the compressor,
The control device determines that the pump down operation end condition is that the detection value of the first pressure detection device is equal to or greater than a first threshold value and the detection value of the second pressure detection device is equal to or less than a second threshold value when, or any one of claims 1-8 to when the detection value of the first pressure detecting device detects values of the first threshold value or more or the second pressure detector is below a second threshold value Item 1. An air conditioner according to item 1. The air according to any one of claims 1 to 9 , further comprising an outdoor unit having at least the compressor, the flow path switching device, the first heat exchanger, the accumulator, and the first opening / closing device. Harmony device. The air conditioner according to any one of claims 1 to 10 , wherein the first opening / closing device is a throttle device in which a valve opening degree is variable. An internal heat exchanger for increasing the degree of supercooling of the refrigerant condensed in the first heat exchanger during cooling operation is provided between the first opening / closing device and the expansion device,
The flow path on the low pressure side of the internal heat exchanger is configured with the bypass pipe,
The air conditioner according to any one of claims 4 to 7 , wherein the second opening / closing device is a throttle device in which a valve opening degree is variable. In place of the second heat exchanger, a heat medium heat exchanger that exchanges heat between the refrigerant and the heat medium is provided,
Air conditioning apparatus according to any one of claim 1 to 12 for air conditioning of the chamber by heat exchange thermal medium by prior Symbol heat medium heat exchanger. The air conditioner according to claim 10 , wherein a plurality of the outdoor units are installed, and a pump down operation and a refrigerant leakage prevention operation are performed for each outdoor unit. Before Kishibo Ri apparatus and provided with a plurality of indoor units having at least the second heat exchanger, the plurality of indoor units, according to claim 1-14 which has an operation mode for performing heating operation and cooling operation at the same time The air conditioning apparatus of any one of Claims.

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