Patent Application
20150176879
The present invention relates to an air-conditioning apparatus that can perform operation such that each of a plurality of indoor units (load-side units) carries out a cooling operation or a heating operation (hereinafter referred to as cooling and heating mixed operation), and more particularly, to an air-conditioning apparatus that improves operation stability by suppressing degradation of the capacity during cooling and heating mixed operation in a low outside air condition.
There has hitherto been an air-conditioning apparatus capable of cooling and heating mixed operation (see, for example, Patent Literature 1). Such an air-conditioning apparatus determines, in accordance with the air condition and operation load, whether load-side units are to be operated in a cooling cycle or a heating cycle. Such an air-conditioning apparatus selects a proper refrigeration cycle in accordance with the load, and realizes the cooling and heating mixed operation.
In the air-conditioning apparatus described in Patent Literature 1, when a load-side unit operates in a heating cycle during the cooling and heating mixed operation, an outdoor heat exchanger functions as an evaporator. Therefore, when the ambient temperature of a heat-source-side unit decreases, the evaporating temperature decreases along with the ambient temperature. At this time, the evaporating temperature of a load-side unit that is performing the cooling operation also decreases. When the evaporating temperature of the load-side unit decreases to 0 degrees C. or less, pipes may be deformed and broken by ice produced by freezing. Further, when frost generated on fins of a heat exchanger mounted in the load-side unit melts, it is not completely received by a drain pan, and this may cause water leakage.
To avoid such a situation, there has already been control that forcibly stops the operation of the load-side unit when the liquid pipe temperature of the load-side unit decreases to be lower than or equal to a predetermined temperature (hereinafter referred to as antifreezing control). However, when antifreezing control is executed, the load-side unit that is performing the heating operation continuously operates, whereas the load-side unit that is performing the cooling operation forcibly stops the operation, and the air-conditioning capacity thereof becomes 0 under suspension. During this time, comfort of the user is impaired. Further, since the stop and the start are repeated, the operation state becomes unstable, and the capacity cannot be exercised continuously.
The present invention has been made in view of the above-described problems, and an object of the invention is to provide an air-conditioning apparatus that enhances operation stability by suppressing degradation of the capacity during cooling and heating mixed operation in a low outside air condition without executing antifreezing control.
An air-conditioning apparatus according to the present invention is capable of cooling and heating mixed operation and is configured such that at least one heat-source-side unit including a compressor and an outdoor heat exchanger is connected to a plurality of load-side units each including an expansion device and an indoor heat exchanger, the plurality of load-side units being connected to the heat-source-side unit in parallel. The air-conditioning apparatus includes an opening and closing valve mounted in the heat-source-side unit to adjust a flow of refrigerant from the load-side units to the outdoor heat exchanger, a heat-source-side expansion device mounted in the heat-source-side unit and provided in parallel with the opening and closing valve, and a controller configured to control at least opening and closing of the opening and closing valve and an opening degree of the heat-source-side expansion device. In a heating main operation mode in which a heating load is dominant in the cooling and heating mixed operation with the plurality of load-side units and under a condition where a liquid pipe temperature of the load-side unit that is performing a cooling operation is within a temperature range of antifreezing control, the controller closes the opening and closing valve and controls the opening degree of the heat-source-side expansion device according to an evaporating temperature of the load-side unit requesting cooling so as to adjust the evaporating temperature to be within a predetermined range.
According to the air-conditioning apparatus of the present invention, the liquid pipe temperature of the load-side unit can be controlled to be within a proper range with the opening degree of the heat-source-side expansion device particularly in a heating main operation mode during cooling and heating mixed operation. Hence, operation stability can be enhanced by suppressing degradation of the capacity during the cooling and heating mixed operation in a low outside side condition without executing antifreezing control.
Embodiment of the present invention will be described below with reference to the drawings.
The air-conditioning apparatus 500 includes a heat-source-side unit 100, a plurality of (two in
The heat-source-side unit 100 has a function of supplying cooling energy or heating energy to the load-side units 300.
In the heat-source-side unit 100, a compressor 1, a four-way switch valve 2 serving as flow switching means, an outdoor heat exchanger 3, and an accumulator 4 are mounted and connected in series to constitute a main refrigerant circuit. In the heat-source-side unit 100, a check valve 5a, a check valve 5b, a check valve 5c, a check valve 5d, a first connecting pipe 110, and a second connecting pipe 111 are also mounted so that the refrigerant flowing into the refrigerant control unit 200 to flow in a fixed direction, regardless of the requests from the load-side units 300. In the heat-source-side unit 100, an expansion device (heat-source-side expansion device) 6 and an opening and closing valve 7 are also mounted.
The compressor 1 sucks a low-temperature and low-pressure gas refrigerant, compresses the refrigerant into a high-temperature and high-pressure gas refrigerant, and performs an air-conditioning operation by circulating the refrigerant in the system. For example, the compressor 1 is preferably formed by a compressor of an inverter type capable of capacity control. However, the compressor 1 is not limited to the compressor of the inverter type capable of capacity control, and may be a compressor of a constant speed type or a compressor formed by a combination of an inverter type and a constant-speed type.
The four-way switch valve 2 is provided on a discharge side of the compressor 1, and switches the refrigerant passage between the cooling operation and the heating operation. The four-way switch valve 2 controls the flow of refrigerant so that the outdoor heat exchanger 3 functions as an evaporator or a condenser in accordance with an operation mode.
The outdoor heat exchanger 3 exchanges heat between a heat medium (for example, ambient air or water) and the refrigerant, functions as an evaporator to evaporate and gasify the refrigerant during heating operation, and functions as a condenser (radiator) to condense and liquefy the refrigerant during cooling operation. The outdoor heat exchanger 3 is generally provided with an unillustrated fan, and controls the condensation capacity or evaporation capacity by the rotation speed of the fan.
The accumulator 4 is provided on a suction side of the compressor 1, and has a function of storing extra refrigerant and a function of separating liquid refrigerant and gas refrigerant.
The first connecting pipe 110 connects the high-pressure pipe 402 on a downstream side of the check valve 5a and the low-pressure pipe 401 on a downstream side of the check valve 5b. The second connecting pipe 111 connects the high-pressure pipe 402 on an upstream side of the check valve 5a and the low-pressure pipe 401 on an upstream side of the check valve 5b. A confluence of the second connecting pipe 111 and the high-pressure pipe 402, a confluence of the first connecting pipe 110 and the high-pressure pipe 402, a confluence of the second connecting pipe 111 and the low-pressure pipe 401, and a confluence of the first connecting pipe 110 and the low-pressure pipe 401 are illustrated as a confluence a, a confluence b (downstream of the confluence a), a confluence c, and a confluence d (downstream of the confluence c), respectively.
The check valve 5b is provided between the confluence c and the confluence d, and allows the refrigerant to flow only in a direction from the refrigerant control unit 200 to the heat-source-side unit 100. The check valve 5a is provided between the confluence a and the confluence b, and allows the refrigerant to flow only in a direction from the heat-source-side unit 100 to the refrigerant control unit 200. The check valve 5c is provided to the first connecting pipe 110, and allows the refrigerant to flow only in a direction from the confluence d to the confluence b. The check valve 5d is provided to the second connecting pipe 111, and allows the refrigerant to flow only in a direction from the confluence c to the confluence a.
The opening and closing valve 7 is provided upstream of the outdoor heat exchanger 3 in the heat-source-side unit 100 (provided to the second connecting pipe 111 on an upstream side of the check valve 5d in the figure), and opening and closing thereof are controlled so as to conduct the refrigerant and so as not to conduct the refrigerant. That is, the opening and closing of the opening and closing valve 7 are controlled to adjust the flow of the refrigerant from the refrigerant control unit 200 to the outdoor heat exchanger 3.
The expansion device 6 is provided in parallel with the opening and closing valve 7, and adjusts the flow rate of refrigerant by controlling the opening degree thereof. That is, the opening degree of the expansion device 6 is controlled to adjust the load-side pipe temperature, more specifically, the evaporating temperature of indoor heat exchangers 22 (indoor heat exchangers 22a, 22b) to be within an arbitrary range.
The heat-source-side unit 100 includes at least a high-pressure sensor 131 for detecting the pressure of refrigerant discharged from the compressor 1, a low-pressure sensor 132 for detecting the pressure of the refrigerant to be sucked into the compressor 1, a discharge-temperature sensor 133 for detecting the temperature of the refrigerant discharged from the compressor 1, and an inlet-pipe temperature sensor 134 for detecting the temperature of refrigerant to flow in the accumulator 4. Information (temperature information and pressure information) detected by these various detection means is sent to a controller 8 for controlling the operation of the air-conditioning apparatus 500, and is used to control the driving frequency of the compressor 1, the rotation speed of the unillustrated fan, switching of the four-way switch valve 2, opening and closing of the opening and closing valve 7, and the opening degree of the expansion device 6.
The refrigerant control unit 200 is interposed between the heat-source-side unit 100 and the load-side units 300, and switches the flow of refrigerant in accordance with an operating situation of the load-side units 300. In
The refrigerant control unit 200 is connected to the heat-source-side unit 100 by the high-pressure pipe 402 and the low-pressure pipe 401, and is connected to the load-side units 300 by the liquid pipes 404 and the gas pipes 403. In the refrigerant control unit 200, a gas-liquid separator 11, first opening and closing valves 12 (first opening and closing valves 12a, 12b), second opening and closing valves 13 (second opening and closing valves 13a, 13b), a first expansion device 14, a second expansion device 15, a first refrigerant heat exchanger 16, and a second refrigerant heat exchanger 17 are mounted. In the refrigerant control unit 200, a connecting pipe 120 is also provided. The connecting pipe 120 branches from a pipe on a downstream side of a primary side of the second refrigerant heat exchanger 17 (side where the refrigerant passing through the first expansion device 14 flows), and is connected to the low-pressure pipe 401.
The gas-liquid separator 11 is provided to the high-pressure pipe 402, and has a function of separating two-phase refrigerant flowing through the high-pressure pipe 402 into gas refrigerant and liquid refrigerant. The gas refrigerant separated by the gas-liquid separator 11 is supplied to the first opening and closing valves 12 via a connecting pipe 121, and the liquid refrigerant is supplied to the first refrigerant heat exchanger 16.
The first opening and closing valves 12 serve to control the supply of refrigerant to the load-side units 300 according to the operation mode, and are provided between the connecting pipe 121 and the gas pipes 403. That is, the first opening and closing valves 12 are connected at one side to the gas-liquid separator 11 and at the other side to the indoor heat exchangers 22 of the corresponding load-side units 300. The opening and closing of the first opening and closing valves 12 are controlled so as to conduct the refrigerant or so as not to conduct the refrigerant.
The second opening and closing valves 13 also serve to control the supply of refrigerant to the load-side units 300 according to the operation mode, and are provided between the gas pipes 403 and the low-pressure pipe 401. That is, the second opening and closing valves 13 are connected at one side to the low-pressure pipe 401 and at the other side to the indoor heat exchangers 22 of the corresponding load-side units 300. The opening and closing of the second opening and closing valves 13 are controlled so as to conduct the refrigerant or so as not to conduct the refrigerant.
The first expansion device 14 is provided to a pipe connecting the gas-liquid separator 11 and the liquid pipes 404, that is, provided between the first refrigerant heat exchanger 16 and the second refrigerant heat exchanger 17, and has a function as a pressure reducing valve and an expansion valve to expand the refrigerant by pressure reduction. The first expansion device 14 is preferably formed by a device capable of variable control of the opening degree, for example, a precise flow rate control device using an electronic expansion valve or inexpensive refrigerant flow rate adjusting means such as a capillary.
The second expansion device 15 is provided to the connecting pipe 120 and on an upstream side of a secondary side of the second refrigerant heat exchanger 17, functions as a pressure reducing valve and an expansion valve, and expands the refrigerant by pressure reduction. Similarly to the first expansion device 14, the second expansion device 15 is preferably formed by a device capable of variable control of the opening degree, for example, a precise flow rate control device using an electronic expansion valve or inexpensive refrigerant flow rate adjusting means such as a capillary.
The first refrigerant heat exchanger 16 exchanges heat between the refrigerant flowing on the primary side (side where the liquid refrigerant separated by the gas-liquid separator 11 flows) and the refrigerant flowing on a secondary side (side where the refrigerant that has flown out of the second refrigerant heat exchanger 17 flows after passing through the second expansion device 15 in the connecting pipe 120).
The second refrigerant heat exchanger 17 exchanges heat between the refrigerant flowing on a primary side (downstream side of the first expansion device 14) and the refrigerant flowing on a secondary side (downstream side of the second expansion device 15).
By mounting the first expansion device 14, the second expansion device 15, the first refrigerant heat exchanger 16, and the second refrigerant heat exchanger 17 in the refrigerant control unit 200, heat is exchanged between the refrigerant flowing in the main circuit (primary side) and the refrigerant flowing in the connecting pipe 120 (secondary side) by the first refrigerant heat exchanger 16 and the second refrigerant heat exchanger 17, so that the refrigerant flowing in the main circuit can be subcooled. By the opening degree of the second expansion device 15, the bypass amount is controlled to achieve proper subcooling at a primary side exit of the second refrigerant heat exchanger 17.
The refrigerant control unit 200 includes at least a temperature sensor 18 for detecting the temperature of the refrigerant pipe (connecting pipe 120) between the second expansion device 15 and a secondary side entrance of the second refrigerant heat exchanger 17, and a temperature sensor 19 for detecting the temperature of the connecting pipe 120 on a downstream side of the secondary side of the first refrigerant heat exchanger 16. Information (temperature information) detected by these various detection means is sent to the controller 8 for controlling the operation of the air-conditioning apparatus 500, and is used to control various actuators. That is, information from the temperature sensor 18 and the temperature sensor 19 is used to control, for example, the opening and closing of the opening and closing valves (first opening and closing valves 12, second opening and closing valves 13) and the opening degrees of the expansion devices (first expansion device 14, second expansion device 15) that are provided in the refrigerant control unit 200.
The load-side units 300 receive cooling energy or heating energy supplied from the heat-source-side unit 100 to bear a cooling load or a heating load. In
In each load-side unit 300, an indoor heat exchanger 22 (indoor heat exchanger 22a, 22b) and an indoor expansion device 21 (indoor expansion device 21a, 21b) are mounted and connected in series. Also, an unillustrated air-sending device is preferably provided to supply air to the indoor heat exchanger 22. However, the indoor heat exchanger 22 may exchange heat between a refrigerant and a heat medium different from the refrigerant, for example, water.
The indoor heat exchanger 22 exchanges heat between a heat medium (for example, ambient air or water) and the refrigerant, functions as a condenser (radiator) to condense and liquefy the refrigerant during heating operation, and functions as an evaporator to evaporate and gasify the refrigerant during cooling operation. The indoor heat exchanger 22 is generally provided with an unillustrated fan, and the condensation capacity or evaporation capacity thereof is controlled by the rotation speed of the fan.
The indoor expansion device 21 functions as a pressure reducing valve and an expansion valve, and expands the refrigerant by pressure reduction. The indoor expansion device 21 is preferably formed by an expansion device capable of variable control of the opening degree, for example, a precise flow rate control device using an electronic expansion valve or inexpensive refrigerant flow rate adjusting means such as a capillary.
Each load-side unit 300 includes at least a temperature sensor 24 (temperature sensor 24a, 24b) for detecting the temperature of the refrigerant pipe between the indoor expansion device 21 and the indoor heat exchanger 22, and a temperature sensor 23 (temperature sensor 23a, 23b) for detecting the temperature of the refrigerant pipe between the indoor heat exchanger 22, and the first opening and closing valve 12 and the second opening and closing valve 13. Information (temperature information) detected by these various detection means is sent to the controller 8 for controlling the operation of the air-conditioning apparatus 500, and is used to control various actuators. That is, information from the temperature sensor 23 and the temperature sensor 24 is used to control, for example, the opening degree of the indoor expansion device 21 and the rotation speed of the unillustrated air-sending device that are provided in the load-side unit 300.
It is only necessary that the compressor 1 can compress sucked refrigerant into a high-pressure state, and the type of the compressor 1 is not particularly limited. For example, the compressor 1 can be formed by utilizing various types such as a reciprocating type, a rotary type, a scroll type, or a screw type. Further, the kind of the refrigerant used in the air-conditioning apparatus 500 is not particularly limited. For example, any of natural refrigerant, such as carbon dioxide, hydrocarbon, or helium, chlorine-free alternative refrigerant, such as HFC410A, HFC407C, or HFC404A, and fluorocarbon refrigerant used in existing products, such as R22 or R134a, may be used.
While the controller 8 for controlling the operation of the air-conditioning apparatus 500 is mounted in the heat-source-side unit 100 in
The operation performed by the air-conditioning apparatus 500 will be described.
The air-conditioning apparatus 500 receives a cooling operation request or a heating operation request from, for example, a remote controller disposed inside the room, and then performs an air-conditioning operation. In correspondence with these requests, there are four operation modes. The four operation modes include a cooling only operation mode in which all the load-side units 300 receive a cooling operation request, a cooling main operation mode in which a cooling operation request and a heating operation request are mixed and it is determined that a load to be processed by the cooling operation is dominant, a heating main operation mode in which a cooling operation request and a heating operation request are mixed and it is determined that a load to be processed by the heating operation is dominant, and a heating only operation mode in which all of the load-side units 300 receive a heating operation request.
A description will be given below of a heating only operation mode and a heating main operation mode in which the evaporating temperature is decreased by the influence of the ambient temperature and the outdoor heat exchanger 3 operates as an evaporator.
A low-temperature and low-pressure refrigerant is compressed by the compressor 1, and is discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way switch valve 2, and flows to the high-pressure pipe 402 via the check valve 5c. After that, this refrigerant flows out of the heat-source-side unit 100. The high-temperature and high-pressure gas refrigerant that has flown out of the heat-source-side unit 100 passes through the gas-liquid separator 11 of the refrigerant control unit 200, and reaches the first opening and closing valves 12 through the connecting pipe 121. The first opening and closing valves 12 are opened, and the second opening and closing valves 13 are closed. The high-temperature and high-pressure gas refrigerant passes through the gas pipes 403, and reaches the load-side units 300.
The gas refrigerant that has flown in the load-side units 300 flows into the indoor heat exchangers 22 (indoor heat exchanger 22a and indoor heat exchanger 22b). Since the indoor heat exchangers 22 function as condensers, the refrigerant is condensed and liquefied by heat exchange with ambient air. At this time, the refrigerant transfers heat to the surroundings, so that an air-conditioned space, such as the inside of the room, is heated. After that, the liquid refrigerant that has flown out of the indoor heat exchangers 22 is subjected to pressure reduction in the indoor expansion devices 21 (indoor expansion device 21a and indoor expansion device 21b), and then flows out of the load-side units 300.
The liquid refrigerant, whose pressure has been reduced in the indoor expansion devices 21, flows through the liquid pipes 404 (liquid pipe 404a and liquid pipe 404b), and flows into the refrigerant control unit 200. The liquid refrigerant that has flown in the refrigerant control unit 200 passes through the second expansion device 15, and reaches the low-pressure pipe 401 through the connecting pipe 120. After flowing out of the refrigerant control unit 200, the refrigerant flowing through the low-pressure pipe 401 returns to the heat-source-side unit 100.
In the heating only operation mode, the opening and closing valve 7 is open and the expansion device 6 is closed. The refrigerant returned to the heat-source-side unit 100 reaches the outdoor heat exchanger 3 via the opening and closing valve 7 and the check valve 5d. Since the outdoor heat exchanger 3 functions as an evaporator, the refrigerant is evaporated and gasified by heat exchange with ambient air. After that, the refrigerant flows out of the outdoor heat exchanger 3, and flows into the accumulator 4 via the four-way switch valve 2. Then, the refrigerant in the accumulator 4 is sucked by the compressor 1, and is circulated in the system, so that the refrigeration cycle is established. Through the above procedure, the air-conditioning apparatus 500 carries out the heating only operation mode.
When a cooling operation request and a heating operation request are mixed as operation requests given to the air-conditioning apparatus 500 and it is determined that the load to be processed by the heating operation is dominant, a heating main operation mode is executed as an operation mode.
Liquid refrigerant passing through the liquid pipe 404a is subcooled by the second refrigerant heat exchanger 17, flows through the liquid pipe 404b, and reaches the load-side unit 300b requesting cooling. The refrigerant that has flown in the load-side unit 300b is subjected to pressure reduction in the indoor expansion device 21b. The refrigerant whose pressure has been reduced by the indoor expansion device 21b flows into the indoor heat exchanger 22b. Since the indoor heat exchanger 22b functions as an evaporator, the refrigerant is evaporated and gasified by heat exchange with ambient air. At this time, the refrigerant removes heat from the surroundings, so that the inside of the room is cooled. After that, the refrigerant that has flown out of the load-side unit 300b flows through the connecting pipe 120 via the second opening and closing valve 13b. This flow of refrigerant joins the refrigerant that has flown through the connecting pipe 120 via the first expansion device 14 and the second expansion device 15 to be subcooled by the second refrigerant heat exchanger 17, and reaches the low-pressure pipe 401.
In the heating main operation mode, the opening and closing valve 7 is open and the expansion device 6 is closed. In this case, the refrigerant, which has flown out of the refrigerant control unit 200 and has flown in the heat-source-side unit 100, flows into the outdoor heat exchanger 3 via the opening and closing valve 7 and the check valve 5d. Since the outdoor heat exchanger 3 functions as an evaporator, the refrigerant is evaporated and gasified by heat exchange with ambient air. After that, the refrigerant flows into the accumulator 4 via the four-way switch valve 2. The refrigerant in the accumulator 4 is sucked by the compressor 1, and is circulated in the system, so that the refrigeration cycle is established. Through the above procedure, the air-conditioning apparatus 500 carries out the heating main operation mode.
At this time, the evaporating temperature is influenced by the ambient temperature of the indoor heat exchanger 22, and the evaporating temperature is lower than the ambient temperature because evaporation and gasification are performed at the ambient temperature. For example, when the ambient temperature is −5 degrees C., the evaporating temperature is a value lower than −5 degrees C., for example, about −11 degrees C. If there is no expansion circuit in the passage from the indoor heat exchanger 22 to the outdoor heat exchanger 3 and it is assumed for explanation that the pipe length is sufficiently short and the pressure loss due to the first opening and closing valve 12 and the second opening and closing valve 13 is negligible, the evaporating temperature of the indoor heat exchanger 22 is equal to the evaporating temperature of the outdoor heat exchanger 3. That is, the evaporating temperature of the indoor heat exchanger 22 decreases as the outside air temperature decreases, and therefore, antifreezing control is executed.
Accordingly, a description will be next given of the evaporating temperature control of the indoor heat exchanger 22 executed by the air-conditioning apparatus 500 using the expansion device 6.
In the heating main operation mode and under a condition where the liquid pipe temperature of the load-side unit 300, which is performing the cooling operation, is within a temperature range of antifreezing control, the opening and closing valve 7 is closed and the expansion device 6 is opened. While the expansion device 6 is preferably formed by a linear expansion valve serving as a variable expansion device, as described above, it may be formed by a combination of a solenoid valve and a capillary, or a combination of opening and closing valves. It is only necessary that the expansion device 6 should be a mechanism that can adjust the expansion amount. The controller 8 detects the evaporating temperature of the indoor heat exchanger 22b with the temperature sensor 24, and adjusts the expansion amount of the expansion device 6 so that the evaporating temperature does not decrease into the antifreezing range.
At this time, when one load-side unit 300 requests cooling, the evaporating temperature can be directly detected with the temperature sensor 24. In general, however, a plurality of load-side units 300 often request cooling. Accordingly, the temperature sensor 18 of the refrigerant control unit 200 detects a representative value of the evaporation temperatures of the load-side units 300. The temperature sensor 18 does not always need to be located between the second expansion device 15 and the second refrigerant heat exchanger 17, and it is only necessary that the temperature sensor 18 should be located in the connecting pipe 120 through which the flows of refrigerant from the load-side units 300 join and reach the low-pressure pipe 401. Instead of the expansion amount control of the expansion device 6 by temperature, the expansion amount can be adjusted by pressure detection with a pressure sensor provided to the connecting pipe 120.
In the heating main operation mode in which the heating load is dominant during the cooling and heating mixed operation using a plurality of load-side units 300, the controller 8 calculates a change amount (opening degree difference) ΔX (Step S101). The change amount ΔX is found as the change amount (opening degree difference) relative to an opening degree X of the expansion device 6 from a saturation temperature Te0 calculated from the low-pressure sensor 132, a detection temperature Te of the temperature sensor 19, and a target temperature Tem of the temperature sensor 19. It is only necessary for the opening degree X of the expansion device 6 to be controlled so that the indoor heat exchangers 22 of the load-side units 300 do not freeze, and the target temperature Tem should be determined in consideration of the influence of pressure loss in the refrigerant control unit 200, the low-pressure pipe 401, and the gas pipes 403. When the pressure loss in the refrigerant control unit 200, the low-pressure pipe 401, and the gas pipes 403 is sufficiently small, Tem can be higher than or equal to the freezing temperature of the pipes (=0 degrees C.), for example, can be equal to 1.
When Te is not equal to Tem (Step S102; N), the controller 8 compares Te and Tem (Step S103). When Te is higher than Tem (Step S103; Y), the controller 8 makes ΔX more than 0 because there is a need to increase the opening degree of the expansion device 6 to increase the pressure difference (Step S104). Conversely, when Te is lower than Tem (Step S103; N), the controller 8 decreases the pressure difference by decreasing the opening degree of the expansion device 6 so that ΔX<0 (Step S105). At this time, for calculation of ΔX, it is conceivable to perform control to open the expansion device 6 at the opening degree corresponding to the temperature difference (Tem-Te) from the target temperature Tem.
As described above, in the air-conditioning apparatus 500, the opening degree of the expansion device 6 is properly controlled so that the temperatures of the load-side units 300 are not within the protective range particularly during the cooling and heating mixed operation. Hence, it is possible to avoid antifreezing control, to suppress degradation of the capacity during the cooling and heating mixed operation in a low outside air condition, and to enhance operation stability.
While one heat-source-side unit 100, one refrigerant control unit 200, and two load-side units 300 are provided in Embodiment, the number of units is not particularly limited. Further, while the present invention is applied to the air-conditioning apparatus 500 in Embodiment, it can also be applied to other systems, including a refrigeration system, which forms a refrigerant circuit using a refrigeration cycle. While the opening and closing valve 7 and the expansion device 6 are preferably connected to the illustrated positions to reduce the pressure loss during cooling operation, they may be provided to the low-pressure pipe 401 on the upstream side of the confluence c (see
A low-temperature and low-pressure refrigerant is compressed by the compressor 1, and is discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 passes through the four-way switch valve 2, and flows to the outdoor heat exchanger 3. Since the outdoor heat exchanger 3 functions as a condenser, the refrigerant is condensed and liquefied by heat exchange with ambient air. After that, the liquid refrigerant that has flown out of the outdoor heat exchanger 3 passes through the high-pressure pipe 402, and flows out of the heat-source-side unit 100 via the check valve 5a.
The high-pressure liquid refrigerant that has flown out of the heat-source-side unit 100 passes through the gas-liquid separator 11 of the refrigerant control unit 200, and flows into the primary side of the first refrigerant heat exchanger 16. The liquid refrigerant that has flown in the primary side of the first refrigerant heat exchanger 16 is subcooled by the refrigerant on the secondary side of the first refrigerant heat exchanger 16. The liquid refrigerant with the increased degree of subcooling is expanded to an intermediate pressure by the first expansion device 14. After that, this liquid refrigerant flows to the second refrigerant heat exchanger 17, and the degree of subcooling thereof is increased further. Then, the liquid refrigerant diverges, and a part thereof flows through the liquid pipes 404a and 404b and flows out of the refrigerant control unit 200.
The liquid refrigerant that has flown out of the refrigerant control unit 200 flows into the load-side units 300a and 300b. The liquid refrigerant that has flown in the load-side units 300a and 300b is expanded by the indoor expansion devices 21a and 21b into a low-temperature two-phase gas-liquid refrigerant. This low-temperature two-phase gas-liquid refrigerant flows into the indoor heat exchangers 22a and 22b. Since the indoor heat exchangers 22a and 22b function as evaporators, the refrigerant is evaporated and gasified by heat exchange with ambient air. At this time, the refrigerant removes heat from the surroundings, and the inside of the room is thereby cooled. After that, the refrigerant that has flown out of the load-side units 300a and 300b passes through the second opening and closing valves 13a and 13b, joins the refrigerant that has flown through the connecting pipe 120 via the first expansion device 14 and the second expansion device 15 to be subcooled in the second refrigerant heat exchanger 17, and reaches the low-pressure pipe 401.
After flowing out of the refrigerant control unit 200, the refrigerant flowing in the low-pressure pipe 401 returns to the heat-source-side unit 100. The gas refrigerant returned to the heat-source-side unit 100 is sucked by the compressor 1 again via the check valve 5b, the four-way switch valve 2, and the accumulator 4. Through the above procedure, the air-conditioning apparatus 500 carries out the cooling only operation mode. That is, the circuit is configured such that the refrigerant does not flow in the second connecting pipe 111 during the cooling only operation. This shows that the opening and closing valve 7 and the expansion device 6 are preferably provided to the second connecting pipe 111.
A low-temperature and low-pressure refrigerant is compressed by the compressor 1, and is discharged as a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 1 flows into the outdoor heat exchanger 3 via the four-way switch valve 2. Since the outdoor heat exchanger 3 functions as a condenser, the refrigerant is condensed and turned into a two-phase state by heat exchange with ambient air. After that, the two-phase gas-liquid refrigerant that has flown out of the outdoor heat exchanger 3 passes through the high-pressure pipe 402, and flows out of the heat-source-side unit 100 via the check valve 5a.
The two-phase gas-liquid refrigerant that has flown out of the heat-source-side unit 100 flows into the gas-liquid separator 11 of the refrigerant control unit 200. The two-phase gas-liquid refrigerant that has flown in the gas-liquid separator 11 is separated into a gas refrigerant and a liquid refrigerant by the gas-liquid separator 11. The gas refrigerant flows out of the gas-liquid separator 11, and then flows into the connecting pipe 121. The gas refrigerant that has flown in the connecting pipe 121 flows through the gas pipe 403b via the first opening and closing valve 12b, and flows into the load-side unit 300b. The gas refrigerant that has flown in the load-side unit 300b heats the air-conditioned space by transferring heat to the surroundings in the indoor heat exchanger 22b. The gas refrigerant itself condenses and liquefies, and flows out of the indoor heat exchanger 22b. The liquid refrigerant that has flown out of the indoor heat exchanger 22b is expanded to an intermediate pressure by the indoor expansion device 21b.
The liquid refrigerant with the intermediate pressure, which has been expanded by the indoor expansion device 21b, flows through the liquid pipe 404b, joins the liquid refrigerant, which has been separated by the gas-liquid separator 11 and has flown via the first refrigerant heat exchanger 16 and the first expansion device 14, and then flows into the second refrigerant heat exchanger 17. The liquid refrigerant that has flown in the second refrigerant heat exchanger 17 further increases the degree of subcooling, flows through the liquid pipe 404a, and flows out of the refrigerant control unit 200. The liquid refrigerant that has flown out of the refrigerant control unit 200 flows into the load-side unit 300a. The liquid refrigerant that has flown in the load-side unit 300a is expanded by the indoor expansion device 21a and is turned into a low-temperature two-phase gas-liquid refrigerant. This low-temperature two-phase gas-liquid refrigerant flows into the indoor heat exchanger 22a, and removes heat from the surroundings to cool the air-conditioned space. The low-temperature two-phase gas-liquid refrigerant itself evaporates and gasifies, and flows out of the indoor heat exchanger 22a.
The gas refrigerant that has flown out of the indoor heat exchanger 22a flows through the gas pipe 403a, flows out of the load-side unit 300a, and then flows into the refrigerant control unit 200. The refrigerant that has flown in the refrigerant control unit 200 passes through the second opening and closing valve 13a, joins the refrigerant, which has flown through the connecting pipe 120 via the first expansion device 14 and the second expansion device 15 to be subcooled by the second refrigerant heat exchanger 17, and then reaches the low-pressure pipe 401.
The refrigerant flowing through the low-pressure pipe 401 flows out of the refrigerant control unit 200, and then returns to the heat-source-side unit 100. The gas refrigerant returned to the heat-source-side unit 100 is sucked by the compressor 1 again via the check valve 5b, the four-way switch valve 2, and the accumulator 4. Through the above procedure, the air-conditioning apparatus 500 carries out the cooling main operation mode. That is, the circuit is configured such that the refrigerant does not flow in the second connecting pipe 111 during the cooling main operation. This shows that the opening and closing valve 7 and the expansion device 6 should be preferably provided to the second connecting pipe 111.
This application is a U.S. national stage application of PCT/JP2012/003515 filed on May 30, 2012, the contents of which are incorporated herein by reference.
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2012/003515 | 5/30/2012 | WO | 00 | 10/3/2014 |
