Patent Application
20160252284
The present invention relates to an air conditioning system for circulating refrigerant between a heat-source-side heat exchanger and a plurality of usage-side heat exchangers, and a method for controlling same.
In a conventional air conditioning apparatus or another air conditioning system, a vapor-compression refrigeration cycle is performed for circulating refrigerant in a refrigerant circuit having a compressor for compressing the refrigerant, a heat-source-side heat exchanger and usage-side heat exchanger for enabling the refrigerant to exchange heat, and a pressure-reducing mechanism for pressure-reducing the refrigerant. Among such air conditioning systems, there are those in which a plurality of indoor units including usage-side heat exchangers are disposed in the same large indoor space of, e.g., a conference hall or the like, in order to sufficiently condition the air in the same indoor space.
In an air conditioning system having a plurality of indoor units in this manner, e.g., the air conditioning apparatus disclosed in Patent Literature 1 (Japanese Laid-open Patent Application No. 2011-257126), operating efficiency is improved without causing the capabilities of the plurality of indoor units to be insufficient, by adjusting the operations of the outdoor unit and the plurality of indoor units.
However, because individual controls are performed on the plurality of indoor units individually, there are cases in which conditions arise such that, due to the operating state, among the plurality of indoor units there are both those that are thermo-ON and those that are thermo-OFF. In such cases, there are times when the operating efficiency of the system has a whole could still be improved even though the operating efficiencies of the individual indoor units is high.
An object of the present invention is for an air conditioning system in which a plurality of indoor units are disposed in the same indoor space to be made more efficient over the entire air conditioning system.
An air conditioning system according to a first aspect of the present invention comprises: a plurality of indoor units installed in the same indoor space, including respective usage-side heat exchangers, and capable of setting set temperatures individually; an outdoor unit including a heat-source-side heat exchanger for conducting heat exchange with refrigerant circulating through the usage-side heat exchangers; and a control device configured so as to perform temperature control of the same indoor space for each indoor unit, using a thermo-ON condition set in advance in accordance with a set temperature, and to relax the thermo-ON condition of thermo-OFF indoor units when there are both thermo-ON indoor units and thermo-OFT indoor units and a predetermined condition has been satisfied.
In the air conditioning system of the first aspect, when there are both thermo-ON indoor units and thermo-OFT indoor units, the thermo-ON condition is relaxed, whereby more indoor units can be switched thermo-ON to increase the number of usage-side heat exchangers conducting heat exchange with refrigerant circulating in the heat-source-side heat exchanger. As a result, due to a greater number of thermo-ON units, heat exchange can be balanced with the apparent area of all the usage-side heat exchangers together having increased, and the differential pressure between evaporation pressure and the condensation pressure of the air conditioning system can be reduced.
An air conditioning system according to a second aspect of the present invention is the air conditioning system according to the first aspect, wherein the control device is configured so as to relax the thermo-ON condition without altering a thermo-OFF condition.
In the air conditioning system of the second aspect, because the thermo-OFT condition is not altered even if the thermo-ON condition is relaxed, thermo-OFF can be carried out at different timings depending on the set temperature that is set in each indoor unit.
An air conditioning system according to a third aspect of the present invention is the air conditioning system according to the first or second aspect, wherein the control device is configured so as to appoint the operating condition of the outdoor unit so as to satisfy the highest increase requirement among the increase requirements for air-conditioning capability from the plurality of indoor units.
In the air conditioning system of the third aspect, the outdoor unit can be operated in response to the highest requirement of air-conditioning capability from among the indoor units, and the air-conditioning capability requirements of all the indoor units are met.
An air conditioning system according to a fourth aspect of the present invention is the air conditioning system according to the third aspect, wherein the control device has required temperature calculation units for calculating required evaporation temperatures or required condensation temperatures of the usage-side heat exchanger for each of the indoor units, and a target value appointing unit for appointing a target evaporation temperature on the basis of the minimum value among the required evaporation temperatures of the indoor units calculated in the required temperature calculation units, or appointing a target condensation temperature on the basis of the maximum value among the required condensation temperatures of the indoor units calculated in the required temperature calculation units.
In the air conditioning system of the fourth aspect, target evaporation temperatures or target condensation temperatures can be appointed for the outdoor unit in response to the highest requirement of air-conditioning capability from among the plurality of indoor units, whereby a target evaporation temperature or a target condensation temperature can be appointed which meets the air-conditioning capability requirements of all of the indoor units.
An air conditioning system according to a fifth aspect of the present invention is the air conditioning system according to any of the first through fourth aspects, wherein the control device is configured so that the predetermined condition is that among the plurality of indoor units, there must be at least one unit that has continued to be thermo-ON for a first elapsed time or longer, and at least one unit that has continued to be thermo-OFF for a second elapsed time or longer.
In the air conditioning system of the fifth aspect, it is possible to prevent a relaxing of the thermo-ON condition due to temporary state in which indoor units that should be thermo-ON have continued to not be thermo-ON for the first elapsed time, or a temporary state in which indoor units that should be thermo-OFF have continued to not be thermo-OFF for the second elapsed time.
An air conditioning system according to a sixth aspect of the present invention is the air conditioning system according to any of the first through fifth aspects, wherein the thermo-ON condition is a condition that the indoor units be thermo-ON when there is a predetermined temperature difference between the set temperature and a control temperature, and the control device is configured so as to relax the thermo-ON condition by reducing the predetermined temperature difference of the thermo-ON condition.
In the air conditioning system of the sixth aspect, a relaxing of the thermo-ON condition can be achieved by a simple operation of altering the predetermined temperature difference relative to the set temperature.
An air conditioning system according to a seventh aspect of the present invention is the air conditioning system according to any of the first through sixth aspects, wherein the plurality of indoor units further include respective air blowers of which the airflow volumes directed to the usage-side heat exchangers can be adjusted; and the control device is configured so as adjust the air blowers for each indoor unit, reduce the airflow volumes when the air-conditioning capabilities are excessive, and increase the airflow volumes when the air-conditioning capabilities are insufficient.
In the air conditioning system of the seventh aspect, the air-conditioning capability of each indoor unit can be autonomously adjusted via the airflow volume of the air blower, and the air-conditioning capability can be autonomously optimized.
An air conditioning system according to an eighth aspect of the present invention is the air conditioning system according to any of the first through seventh aspects, wherein the plurality of indoor units further include respective expansion mechanisms capable of adjusting the degrees of superheat or the degrees of subcooling in the outlet sides of the usage-side heat exchangers; and the control device is configured so as to adjust the opening degrees of the expansion mechanisms in each indoor unit, reduce the degrees of superheat or degrees of subcooling when the air-conditioning capabilities are excessive, and increase the degrees of superheat or degrees of subcooling when the air-conditioning capabilities are insufficient.
In the air conditioning system of the eighth aspect, the air-conditioning capability in each indoor unit can be autonomously adjusted by adjusting the opening degree of the expansion mechanism.
An air conditioning system according to a ninth aspect of the present invention is the air conditioning system according to any of the first through eighth aspects, wherein the control device is centralized controllers which acquire data from the outdoor unit and the plurality of indoor units, and send data to the outdoor unit and the plurality of indoor units.
In the air conditioning system of the ninth aspect, the outdoor unit and the indoor units can be collectively managed by centralized controllers.
A method for controlling an air conditioning system according to a tenth aspect of the present invention is a method for controlling an air conditioning system comprising: a plurality of indoor units installed in the same indoor space, including respective usage-side heat exchangers, and capable of setting set temperatures individually; and an outdoor unit including a heat-source-side heat exchanger for conducting heat exchange with refrigerant circulating through the usage-side heat exchangers; the method for controlling an air conditioning system having a first step of causing temperature control of the same indoor space to be performed in each indoor unit, using a thermo-ON condition set in advance in accordance with the set temperatures, and a second step of relaxing the thermo-ON condition of thermo-OFF indoor units when the indoor units include both those that are thermo-ON and those that are thermo-OFT and a predetermined condition is satisfied.
In the method for controlling an air conditioning system of the tenth aspect, when there are both thermo-ON indoor units and thermo-OFF indoor units, the thermo-ON condition is relaxed, whereby more indoor units can be switched thermo-ON to increase the number of usage-side heat exchangers conducting heat exchange with refrigerant circulating in the heat-source-side heat exchanger. As a result, there are more thermo-ON indoor units, whereby heat exchange can be balanced with the apparent area of all the usage-side heat exchangers together having increased, and the differential pressure between the evaporation pressure and the condensation pressure of the air conditioning system can be reduced.
In the air conditioning system according to the first aspect of the present invention or the method for controlling an air conditioning system according to the tenth aspect, the differential pressure between the evaporation pressure and the condensation pressure of the air conditioning system can be reduced to improve the efficiency of the entire air conditioning system.
In the air conditioning system of the second aspect, thermo-OFF can be carried out at different timings depending on the set temperature that is set in each indoor unit, and efficiency can be improved while carrying out operations conforming to the requirements of each of the indoor units.
In the air conditioning system of the third aspect, efficiency can be improved while preventing the air-conditioning capabilities from being insufficient in some indoor units.
In the air conditioning system of the fourth aspect, a target evaporation temperature or a target condensation temperature can be appointed which meets the air-conditioning capability requirements of all of the indoor units, and efficiency can he improved while preventing the air-conditioning capabilities from being insufficient in some indoor units.
In the air conditioning system of the fifth aspect, efficiency can be improved while suppressing temperature imbalances in the same indoor space.
In the air conditioning system of the sixth aspect, control of an air conditioning systema that readily turns thermo-ON can be achieved in a simple manner.
In the air conditioning system of the seventh aspect, air-conditioning capabilities can be autonomously optimized via the airflow volumes of the air blowers, and loss of efficiency due to altering of the thermo-ON condition can be suppressed in each indoor unit.
In the air conditioning system of the eighth aspect, air-conditioning capabilities can be autonomously optimized via the opening degrees of the expansion mechanisms, and loss of efficiency due to altering of the thermo-ON condition can be suppressed in each indoor unit.
In the air conditioning system of the ninth aspect, the entire air conditioning system is easily harmonized.
An air conditioning apparatus and a method for controlling same are described below, with reference to the drawings, as an example of the air conditioning system and the method for controlling same according to the present invention.
(1) Configuration of Air Conditioning Apparatus
(1-1) Indoor Units
The indoor units 40, 50, 60 are installed in one room 1 such as, e.g., a conference room of a building by being embedded in, suspended from, or otherwise attached to the ceiling of the room, or by being mounted on or otherwise attached to a wall of the room. The indoor units 40, 50, 60 are connected to the outdoor unit 20 via the liquid refrigerant communication tube 71 and the gas refrigerant communication tube 72, and the indoor units constitute part of the refrigerant circuit 11.
Next, the configurations of the indoor units 40, 50, 60 are described. Because the indoor unit 40 and the indoor units 50, 60 have the same configuration, only the configuration of the indoor unit 40 is described here, and the configurations of the indoor units 50, 60, being denoted with symbols numbering in the fifties and sixties in place of the symbols numbering in the forties indicating the components of the indoor unit 40, are not described.
The indoor unit 40 has primarily an indoor-side refrigerant circuit 11a constituting part of the refrigerant circuit 11 (the indoor unit 50 has an indoor-side refrigerant circuit 11b and the indoor unit 60 has an indoor-side refrigerant circuit 11c). This indoor-side refrigerant circuit 11a has primarily an indoor expansion valve 41 as an expansion mechanism and an indoor heat exchanger 42 as a usage-side heat exchanger. In the present embodiment, indoor expansion valves 41, 51, 61 are provided as expansion mechanisms to the indoor units 40, 50, 60 respectively, but the embodiment is not limited as such, and an expansion mechanism (including an expansion valve) may be provided to the outdoor unit 20, or to a connection unit independent of the indoor units 40, 50, 60 and the outdoor unit 20.
The indoor expansion valve 41 is an electric expansion valve connected to the liquid side of the indoor heat exchanger 42 in order to adjust or otherwise manipulate the flow rate of refrigerant flowing within the indoor-side refrigerant circuit 11a, and is also capable of blocking the passage of refrigerant.
The indoor heat exchanger 42 is a cross-fin-type fin-and-tube heat exchanger configured from, e.g., a heat transfer tube and numerous fins, and this heat exchanger functions as an evaporator of refrigerant to cool indoor air during an air-cooling operation, and functions as a condenser of refrigerant to heat indoor air during an air-heating operation.
The indoor unit 40 has an indoor fan 43 as an air blower for drawing indoor air into the unit, and supplying heat-exchanged indoor air as supply air into the room after the air has exchanged heat with refrigerant in the indoor heat exchanger 42. The indoor fan 43 is a fan capable of varying the airflow volume of air supplied to the indoor heat exchanger 42 within a predetermined airflow volume range, and is a centrifugal fan, multi-blade fan, or the like driven by a motor 43m composed of, e.g., a DC fan motor or the like. The indoor fan 43 can be selectively set to any of the following modes: constant-airflow-volume mode in which the airflow volume is set to one of three constant airflow volumes including low airflow having the lowest airflow volume, high airflow having the highest airflow volume, and medium airflow of an intermediate extent between low airflow and high airflow; automatic-airflow-volume-control mode in which the airflow volume is automatically varied from low airflow to high airflow in accordance with the degree of superheat SH, the degree of subcooling SC, and/or other factors; and airflow-volume-setting mode in which the airflow volume is manually varied through a remote controller or another input device. Specifically, when a user selects either “low airflow,” “medium airflow,” or “high airflow” using, e.g., a remote controller, the mode will be constant-airflow-volume mode in which the airflow volume is constant at low airflow, and when a user selects “automatic,” the mode will be automatic-airflow-volume-control mode in which the airflow volume is varied automatically in accordance with the operating state. A description is given here of the configuration whereby the fan tap of the airflow volume of the indoor fan 43 is switched among the three levels “low airflow,” “medium airflow,” and “high airflow.” The indoor fan airflow volume Ga, which is the airflow volume of the indoor fan 43, can be derived from a calculation using, e.g., the rotational speed of the motor 43m as a parameter. Alternative methods include deriving the indoor fan airflow volume Ga from a calculation based on the electric current value of the motor 43m, deriving the indoor fan airflow volume Ga from a calculation based on the set fan tap, and other methods.
Various sensors are also provided to the indoor unit 40. On the liquid side of the indoor heat exchanger 42, a liquid line temperature sensor 44 is provided for detecting the temperature of the refrigerant (i.e., the refrigerant temperature corresponding to the condensation temperature Tc during the air-heating operation or the evaporation temperature Te during the air-cooling operation). On the gas side of the indoor heat exchanger 42, a gas line temperature sensor 45 is provided for detecting the temperature of the refrigerant. On the intake port side for indoor air of the indoor unit 40, an indoor temperature sensor 46 is provided for detecting the temperature of indoor air flowing into the unit (i.e., the indoor temperature Tr). For example, thermistors can be used for the liquid line temperature sensor 44, the gas line temperature sensor 45, and the indoor temperature sensor 46. The indoor unit 40 also has an indoor-side control device 47 for controlling the actions of the components constituting the indoor unit 40. The indoor-side control device 47 has an air-conditioning capability calculation unit 47a for calculating the current air-conditioning capability and other parameters in the indoor unit 40, and a required temperature calculation unit 47b for calculating, on the basis of the current air-conditioning capability, the required evaporation temperature Ter or required condensation temperature Tcr needed to achieve said capability (see
(1-2) Outdoor Unit
The outdoor unit 20 is installed on the outside of a building or the like and is connected to the indoor units 40, 50, 60 via the liquid refrigerant communication tube 71 and the gas refrigerant communication tube 72, and the outdoor unit 20 together with the indoor units 40, 50, 60 constitutes the refrigerant circuit 11.
Next, the configuration of the outdoor unit 20 is described. The outdoor unit 20 has primarily an outdoor-side refrigerant circuit 11d constituting part of the refrigerant circuit 11. This outdoor-side refrigerant circuit 11d has primarily a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23 as a heat-source-side heat exchanger, an outdoor expansion valve 38 as an expansion mechanism, an accumulator 24, a liquid-side shutoff valve 26, and a gas-side shutoff valve 27.
The compressor 21 is a compressor of which the operating capacity can be varied, and is a positive-displacement compressor driven by a motor 21m of which the rotational speed is controlled by an inverter. There is only one compressor 21 of the outdoor unit 20 depicted here, but there can be two or more compressors in cases such as when there is a large number of indoor units connected.
The four-way switching valve 22 is a valve for switching the direction of refrigerant flow. During the air-cooling operation, the four-way switching valve 22 connects the discharge side of the compressor 21 and the gas side of the outdoor heat exchanger 23, and connects the intake side of the compressor 21 (specifically, the accumulator 24) and the gas refrigerant communication tube 72 side (air-cooling operation state: refer to the solid lines of the four-way switching valve 22 in
The outdoor heat exchanger 23 is, e.g., a cross-fin-type fin-and-tube heat exchanger, and is a device for enabling heat exchange between air and refrigerant in order to use air as a heat source. The outdoor heat exchanger 23 is a heat exchanger that functions as a condenser of refrigerant during the air-cooling operation, and functions as an evaporator of refrigerant during the air-heating operation. The gas side of the outdoor heat exchanger 23 is connected to the four-way switching valve 22, and the liquid side is connected to the outdoor expansion valve 38.
The outdoor expansion valve 38 is an electric expansion valve disposed on what is during the air-cooling operation the downstream side of the outdoor heat exchanger 23 in the direction of refrigerant flow in the refrigerant circuit 11, in order to adjust the pressure, flow rate, and/or other characteristics of the refrigerant flowing within the outdoor-side refrigerant circuit 11d. In other words, the outdoor expansion valve 38 is connected to the liquid side of the outdoor heat exchanger 23.
The outdoor unit 20 has an outdoor fan 28 as an air blower for drawing outdoor air into the unit, and discharging the air out of the room after the air has exchanged heat with the refrigerant in the outdoor heat exchanger 23. This outdoor fan 28 is a fan capable of varying the airflow volume of air supplied to the outdoor heat exchanger 23, and is a propeller fan or the like driven by a motor 28m composed of, e.g., a DC fan motor or the like.
The liquid-side shutoff valve 26 and the gas-side shutoff valve 27 are valves provided to the ports connecting with the liquid refrigerant communication tube 71 and the gas refrigerant communication tube 72. The liquid-side shutoff valve 26 is disposed on what is during the air-cooling operation the downstream side of the outdoor expansion valve 38 and the upstream side of the liquid refrigerant communication tube 71 in the direction of refrigerant flow in the refrigerant circuit 11, and is capable of blocking the passage of refrigerant. The gas-side shutoff valve 27 is connected to the four-way switching valve 22 and is capable of blocking the passage of refrigerant.
The outdoor unit 20 is provided with an intake pressure sensor 29 for detecting the intake pressure of the compressor 21 (i.e., the refrigerant pressure corresponding to the evaporation pressure Pe during the air-cooling operation), a discharge pressure sensor 30 for detecting the discharge pressure of the compressor 21 (i.e., the refrigerant pressure corresponding to the condensation pressure Pc during the air-heating operation), an intake temperature sensor 31 for detecting the intake temperature of the compressor 21, and a discharge temperature sensor 32 for detecting the discharge temperature of the compressor 21. Provided on the intake port side for outdoor air of the outdoor unit 20 is an outdoor temperature sensor 36 for detecting the temperature of outdoor air (i.e., the outdoor temperature) flowing into the unit. For example, thermistors can be used for the intake temperature sensor 31, the discharge temperature sensor 32, and the outdoor temperature sensor 36. The outdoor unit 20 also has an outdoor-side control device 37 for controlling the actions of the components constituting the outdoor unit 20. The outdoor-side control device 37 has a target value appointing unit 37a for appointing a target evaporation temperature Tet or a target condensation temperature Tct (alternatively, a target evaporation temperature difference ΔTet or a target condensation temperature difference ΔTct) for controlling the operating capacity of the compressor 21, as shown in
The operation control device 80 is connected so as to be able to receive the detection signals of the intake pressure sensor 29, the discharge pressure sensor 30, the intake temperature sensor 31, the discharge temperature sensor 32, the outdoor temperature sensor 36, the liquid line temperature sensors 44, 54, 64, the gas line temperature sensors 45, 55, 65, and the indoor temperature sensors 46, 56, 66, as shown in
(1-3) Refrigerant Communication Tube
The refrigerant communication tubes 71, 72 are refrigerant tubes constructed on site when the air conditioning apparatus 10 is installed in a building or another installation location, and tubes of various lengths and/or diameters are used depending on the installation location, the combination of the models of the outdoor unit and indoor units, and other installation conditions. For example, when a new air conditioning apparatus 10 is installed in a building or the like, the air conditioning apparatus 10 is filled with the proper quantity of refrigerant depending on the lengths and diameters of the refrigerant communication tubes 71, 72, and/or other installation conditions.
As described above, the indoor-side refrigerant circuits 11a, 11b, 11c, the outdoor-side refrigerant circuit 11d, and the refrigerant communication tubes 71, 72 are connected, constituting the refrigerant circuit 11 of the air conditioning apparatus 10. The air conditioning apparatus 10 is designed so that operation is performed by the operation control device 80 configured from the indoor-side control devices 47. 57, 67 and the outdoor-side control device 37, while the air-cooling operation and the air-heating operation are switched by the four-way switching valve 22, and the various devices of the outdoor unit 20 and the indoor units 40, 50, 60 are controlled in accordance with operating loads of the indoor units 40, 50, 60.
(2) Actions of Air Conditioning Apparatus
During the air-cooling operation and the air-heating operation in the air conditioning apparatus 10, indoor temperature control is performed on the indoor units 40, 50, 60, in which the indoor temperatures Tr1, Tr2, Tr3 are brought nearer to set temperatures Ts1, Ts2, Ts3 set individually for each of the indoor units 40, 50, 60 by a user via a remote controller or another input device. In this indoor temperature control, when the indoor fans 43, 53, 63 are set to automatic-airflow-volume-control mode, the airflow volume of the indoor fan 43 and the opening degree of the indoor expansion valve 41 are adjusted so that the indoor temperature Tr1 approaches the set temperature Ts1, the airflow volume of the indoor fan 53 and the opening degree of the indoor expansion valve 51 are adjusted so that the indoor temperature Tr2 approaches the set temperature Ts2, and the airflow volume of the indoor fan 63 and the opening degree of the indoor expansion valve 61 are adjusted so that the indoor temperature Tr3 converges on the set temperature Ts3.
When the indoor fans 43, 53, 63 are set to constant-airflow-volume mode, the opening degree of the indoor expansion valve 41 is adjusted an that the indoor temperature Tr' approaches the set temperature Ts1, the opening degree of the indoor expansion valve 51 is adjusted so that the indoor temperature Tr2 approaches the set temperature Ts2, and the opening degree of the indoor expansion valve 61 is adjusted so that the indoor temperature Tr3 approaches the set temperature Ts3. What is controlled by adjusting the opening degrees of the indoor expansion valves 41, 51, 61 is the degree of superheat in the outlets of the indoor heat exchangers 42, 52, 62 during the air-cooling operation, and the degree of subcooling in the outlets of the indoor heat exchangers 42, 52, 62 during the air-heating operation.
(2-1) Air-Cooling Operation
First, the air-cooling operation is described using
During the air-cooling operation, the four-way switching valve 22 is in the state indicated by the solid lines in
The target degrees of superheat SHt1, SHt2, Sht3 are set to the optimal temperature values in order for the indoor temperatures Tr1, Tr2, Tr3 to approach the set temperatures Ts1, Ts2, Ts3 within a predetermined degree of superheat range. The degrees of superheat SH1, SH2, SH3 of the refrigerant in the outlets of the indoor heat exchangers 42, 52, 62 are respectively detected by subtracting the refrigerant temperature values (corresponding to the evaporation temperature Te) detected by the liquid line temperature sensors 44, 54, 64 from the refrigerant temperature values detected by the gas line temperature sensors 45, 55, 65. The degrees of superheat SH1, SH2, SH3 of the refrigerant in the outlets of the indoor heat exchangers 42, 52, 62 are not limited to being detected by the above method, and may be detected by converting the intake pressure of the compressor 21 detected by the intake pressure sensor 29 to a saturation temperature value corresponding to the evaporation temperature Te, and subtracting this refrigerant saturation temperature value from the refrigerant temperature values detected by the gas line temperature sensors 45, 55, 65.
Though not employed in the present embodiment, the degrees of superheat SH1, SH2, SH3 of the refrigerant in the outlets of the indoor heat exchangers 42, 52, 62 may be detected by providing temperature sensors for detecting the temperatures of the refrigerant flowing within the indoor heat exchangers 42, 52, 62, and subtracting the refrigerant temperature values corresponding to the evaporation temperatures Te detected by these temperature sensors from the refrigerant temperature values detected by the gas line temperature sensors 45, 55, 65.
When the compressor 21, the outdoor fan 28, and the indoor fans 43, 53, 63 are operated during this state of the refrigerant circuit 11, low-pressure gas refrigerant is drawn into the compressor 21 and compressed to high-pressure gas refrigerant. The high-pressure gas refrigerant is then sent to the outdoor heat exchanger 23 via the four-way switching valve 22, and the refrigerant exchanges heat with outdoor air supplied by the outdoor fan 28 and condenses to high-pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the indoor units 40, 50, 60 via the liquid-side shutoff valve 26 and the liquid refrigerant communication tube 71.
The high-pressure liquid refrigerant sent to the indoor units 40, 50, 60 is pressure-reduced nearly to the intake pressure of the compressor 21 by the indoor expansion valves 41, 51, 61, becoming low-pressure gas-liquid two-phase refrigerant which is sent to the indoor heat exchangers 42, 52, 62, and the refrigerant exchanges heat with indoor air in the indoor heat exchangers 42, 52, 62 and evaporates to low-pressure gas refrigerant.
This low-pressure gas refrigerant is sent to the outdoor unit 20 via the gas refrigerant communication tube 72, and the refrigerant flows through the gas-side shutoff valve 27 and the four-way switching valve 22 into the accumulator 24. The low-pressure gas refrigerant that has flowed into the accumulator 24 is again drawn into the compressor 21. An air-cooling operation can be performed in the air conditioning apparatus 10, in which the outdoor heat exchanger 23 is made to function as a condenser of the refrigerant compressed in the compressor 21, and the indoor heat exchangers 42, 52, 62 are made to function as evaporators of the refrigerant condensed in the outdoor heat exchanger 23 and then sent through the liquid refrigerant communication tube 71 and the indoor expansion valves 41, 51, 61. In the air conditioning apparatus 10, because the indoor units 40, 50, 60 have no mechanisms for adjusting the pressure of the refrigerant in the gas sides of the indoor heat exchangers 42, 52, 62, the indoor heat exchangers 42, 52, 62 all share a common evaporation pressure Pe.
Energy conservation control is performed during this air-cooling operation in the air conditioning apparatus 10. The energy conservation control during the air-cooling operation is described below on the basis of the flowchart of
First, in step S11, the air-conditioning capability calculation units 47a, 57a, 67a of the indoor-side control devices 47, 57, 67 of the indoor units 40, 50, 60 respectively calculate the air-conditioning capabilities Q11, Q12, Q13 in the indoor units 40, 50, 60 on the basis of temperature differences ΔTer1, ΔTer2, ΔTer3 which are the temperature differences between the indoor temperatures Tr1, Tr2, Tr3 and the evaporation temperature Te, indoor fan airflow volumes Ga1, Ga2, Ga3 caused by the indoor fans 43, 53, 63, and the degrees of superheat SH1, SH2, SH3, at that point in time. The calculated air-conditioning capabilities Q11, Q12, Q13 are stored respectively in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67. The air-conditioning capabilities Q11, Q12, Q13 may also be calculated using the evaporation temperature Te instead of the temperature differences ΔTer1, ΔTer2, ΔTer3.
In step S12, the air-conditioning capability calculation units 47a, 57a, 67a respectively calculate displacements ΔQ1, ΔQ2, ΔQ3 of the air-conditioning capabilities in the indoor space on the basis of the indoor temperatures Tr1, Tr2, Tr3 calculated respectively by the indoor temperature sensors 46, 56, 66, and the temperature differences ΔT1, ΔT2, ΔT3 with the set temperatures Ts1, Ts2, Ts3 set by a user through a remote controller or the like at the time. The air-conditioning capability calculation units 47a, 57a, 67a then respectively calculate required capabilities Q21, Q22, Q23 by adding the displacements to the air-conditioning capabilities Q11, Q12, Q13. The calculated required capabilities Q21, Q22, Q23 are respectively stored in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67.
Though not shown in
Specifically, due to indoor temperature control, the air-conditioning capabilities of the indoor units 40, 50, 60 are maintained respectively between the above-described air-conditioning capabilities Q11, Q12, Q13 and the required capabilities Q21, Q22, Q23. Essentially, the equivalent of the amount of heat exchanged in the indoor heat exchangers 42, 52, 62 is between the air-conditioning capabilities Q11, Q12, Q13 of the indoor units 40, 50, 60 and the required capabilities Q21, Q22, Q23. Therefore, during energy conservation control when sufficient time has elapsed after the start of operation and a nearly steady state has been reached, the air-conditioning capabilities Q11, Q12, Q13 of the indoor units 40, 50, 60 and/or the required capabilities Q21, Q22, Q23 are nearly equivalent to the current amounts of heat exchanged in the indoor heat exchangers 42, 52, 62.
In step S13, a confirmation is made as to whether the airflow-volume set mode in the remote controllers of the indoor fans 43, 53, 63 is the automatic-airflow-volume-control mode or the constant-airflow-volume mode. When the airflow-volume set mode of the indoor fans 43, 53, 63 is the automatic-airflow-volume-control mode, the sequence transitions to step S14, and when the mode is the constant-airflow-volume mode, the sequence transitions to step S15.
In step S14, the required temperature calculation units 47b, 57b, 67b respectively calculate required evaporation temperatures Ter1, Ter2, Ter3 of the indoor units 40, 50, 60 on the basis of the required capabilities Q21, Q22, Q23, airflow volume maximum values GaMAX1, GaMAX2, GaMAX3 (the airflow volumes in “high airflow”) of the indoor fans 43, 53, 63, and degree of superheat minimum values SHmin1, SHmin2, SHmin3. The required temperature calculation units 47b, 57b, 67b also respectively calculate evaporation temperature differences ΔTe1, ΔTe2, ΔTe3, which are the required evaporation temperatures Ter1, Ter2, Ter3 less the evaporation temperatures Te1, Te2, Te3 detected by the liquid line temperature sensors 44, 54, 64 at the time. The term “degree of superheat minimum value SHmin” used herein refers to the minimum value of the range in which the degree of superheat can be set by adjusting the opening degrees of the indoor expansion valves 41, 51, 61, the respective values SHmin1, SHmin2, SHmin3 are set according to the model, and the set values are sometimes different from each other and sometimes the same as each other. In the indoor units 40, 50, 60, when the airflow volumes of the indoor fans 43, 53, 63 and/or the degrees of superheat are brought to the airflow volume maximum values GMAX1, GaMAX2, GaMAX3 and the degree of superheat minimum values SHmin1, SHmin2, SHmin3, if they are not currently at the airflow volume maximum values GaMAX1, GaMAX2, GaMAX3 and the degree of superheat minimum values SHmin1, SHmin2, SHmin3, it is possible to create a state in which greater amounts of heat exchanged than the current amounts are exhibited in the indoor heat exchangers 42, 52, 62. Therefore, an operating state amount involving the airflow volume maximum values GaMAX1, GaMAX2, GaMAX3 and the degree of superheat minimum values SHmin1, SHmin2, SHmin3 is an operating state amount that can create a state in which greater amounts of heat exchanged than the current amounts are exhibited in the indoor heat exchangers 42, 52, 62. The calculated evaporation temperature differences ΔTe1, ΔTe2, ΔTe3 are then stored respectively in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67.
In step S15, the required temperature calculation units 47b, 57b, 67b respectively calculate the required evaporation temperatures Ter1, Ter2, Ter3 of the indoor units 40, 50, 60 on the basis of the required capabilities Q21, Q22, Q23, the constant airflow volumes Ga1, Ga2, Ga3 (e.g., the airflow volumes in “medium airflow”) of the indoor fans 43, 53, 63, and the degree of superheat minimum values SHmin1, SHmin2, SHmin3. The required temperature calculation units 47b, 57b, 67b also respectively calculate the evaporation temperature differences ΔTe1, ΔTe2, ΔTe3, which are the required evaporation temperatures Ter1, Ter2, Ter3 less the evaporation temperature Te detected by the liquid line temperature sensors 44, 54, 64 at the time. The calculated evaporation temperature differences ΔTe1, ΔTe2, ΔTe3 are stored respectively in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67. In this step S15, the constant airflow volumes Ga1, Ga2, Ga3 are employed instead of the airflow volume maximum values GaMAX1, GaMAX2, GaMAX3, but the purpose of this is to prioritize the airflow volumes set by the user, and the airflow volumes will he recognized as airflow volume maximum values within the range set by the user,
In step S16, the evaporation temperature differences ΔTe1, ΔTe2, ΔTe3, which had been stored respectively in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67 in steps S14 and S15, are sent to the outdoor-side control device 37 and stored in the memory 37b of the outdoor-side control device 37. The target value appointing unit 37a of the outdoor-side control device 37 then appoints a minimum evaporation temperature difference ΔTemin, which is the minimum among the evaporation temperature differences ΔTe1, ΔTe2, ΔTe3, as the target evaporation temperature difference ΔTet. For example, when the evaporation temperature differences ΔTe1, ΔTe2, ΔTe3 of the indoor units 40, 50, 60 are 1° C., 0° C., and −2° C., the ΔTemin is −2° C.
In step S17, the operating capacity of the compressor 21 is controlled so that the evaporation temperature nears the new target evaporation temperature Tet updated with the ΔTemin. Thus, as a result of the operating capacity of the compressor 21 being controlled on the basis of the target evaporation temperature difference ΔTet, in the indoor unit (assume the indoor unit 40 in this case) that had calculated the minimum evaporation temperature difference ΔTemin employed as the target evaporation temperature difference ΔTet, the indoor fan 43 is adjusted so as to reach the airflow volume maximum value GaMAX1 when set to the automatic-airflow-volume-control mode, and the indoor expansion valve 41 is adjusted so that the degree of superheat SH in the outlet of the indoor heat exchanger 42 reaches the degree of superheat minimum value SHmin1.
Air-cooling heat exchange functions, which differ for each of the indoor units 40, 50, 60 and take into account the relationships of the air-conditioning (required) capabilities Q11, Q12, Q13 (Q21, Q22, Q23), airflow volumes Ga1, Ga2, Ga3, degrees of superheat SH1, SH2, SH3, and temperature differences ΔTer1, ΔTer2, ΔTer3 of each of the indoor units 40, 50, 60, are used to calculate the air-conditioning capabilities Q12, Q13 in step S11 and to calculate the evaporation temperature differences ΔTe1, ΔTe2, ΔTe3 in step S14 or S15. These air-cooling heat exchange functions are relational expressions associated with the air-conditioning (required) capabilities Q11, Q12, Q13 (Q21, Q22, Q23), airflow volumes Ga1, Ga2, Ga3, degrees of superheat SH1, SH2, SH3, and temperature differences ΔTer1, ΔTer2, ΔTer3 representing the characteristics of the indoor heat exchangers 42, 52, 62, and these functions are stored respectively in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67 of the indoor units 40, 50, 60. One variable among the air-conditioning (required) capabilities Q11, Q12, Q13 (Q21, Q22, Q23), airflow volumes Ga1, Ga2, Ga3, degrees of superheat SH1, SH2, SH3, and temperature differences ΔTer1, ΔTer2, ΔTer3 is determined by inputting the other three variables into the air-cooling heat exchange functions. The evaporation temperature differences ΔTe1, ΔTe2, ΔTe3 can thereby be brought to the proper values with precision, and the target evaporation temperature difference ΔTet can be accurately determined. Therefore, excessive increases of the evaporation temperature Te can be prevented. Therefore, excess and deficiency in the air-conditioning capabilities of the indoor units 40, 50, 60 can he prevented, the optimal states of the indoor units 40, 50, 60 can be achieved quickly and stably, and a greater energy conservation effect can be exhibited.
The target evaporation temperature let is updated on the basis of the target evaporation temperature difference ΔTet in this flow to control the operating capacity of the compressor 21, but the target evaporation temperature is not limited to the target evaporation temperature difference ΔTet, the target value appointing unit 37a may appoint the minimum value of the required evaporation temperature Ter calculated in the indoor units 40, 50, 60 as the target evaporation temperature Tet, and the operating capacity of the compressor 21 may be controlled on the basis of the appointed target evaporation temperature Tet.
(2-2) Air-Heating Operation
Next, the air-heating operation is described using
During the air-heating operation, the four-way switching valve 22 is in the state indicated by the dashed lines in FIG I (the air-heating operation state), i.e., a state in which the discharge side of the compressor 21 is connected to the gas sides of the indoor heat exchangers 42, 52, 62 via the gas-side shutoff valve 27 and the gas refrigerant communication tube 72, and the intake side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23. The opening degree of the outdoor expansion valve 38 is adjusted in order to depressurize the refrigerant flowing into the outdoor heat exchanger 23 to a pressure at which the refrigerant can be evaporated (i.e., the evaporation pressure Pe) in the outdoor heat exchanger 23. The liquid-side shutoff valve 26 and the gas-side shutoff valve 27 are open. The opening degrees of the indoor expansion valves 41, 51, 61 are adjusted so that the degrees of subcooling SC1, SC2, SC3 of the refrigerant in the outlets of the indoor heat exchangers 42, 52, 62 respectively reach target degrees of subcooling SCt1, SCt2, SCt3. The target degrees of subcooling SCt1, SCt2, SCt3 are set to optimal temperature values in order for the indoor temperatures Tr1, Tr2, Tr3 to approach the set temperatures Ts1, Ts2, Ts3 within the degree of subcooling range specified according to the operating state at that time. The degrees of subcooling SC1, SC2, SC3 of the refrigerant in the outlets of the indoor heat exchangers 42, 52, 62 are detected by converting the discharge pressure Pd of the compressor 21 detected by the discharge pressure sensor 30 to a saturation temperature value corresponding to the condensation temperature Tc, and subtracting the refrigerant temperature values detected by the liquid line temperature sensors 44, 54, 64 from this refrigerant saturation temperature value.
Though not employed in the present embodiment, temperature sensors may be provided for detecting the temperature of the refrigerant flowing within the indoor heat exchangers 42, 52, 62, and the degrees of subcooling SC1, SC2, SC3 of the refrigerant in the outlets of the indoor heat exchangers 42, 52, 62 may be detected by subtracting the refrigerant temperature values corresponding to the condensation temperature Tc detected by these temperature sensors from the refrigerant temperature values detected by the liquid line temperature sensors 44, 54, 64.
When the compressor 21, the outdoor fan 28, and the indoor fans 43, 53, 63 are operated in this state of the refrigerant circuit 11, low-pressure gas refrigerant is drawn into the compressor 21 and compressed to high-pressure gas refrigerant, which is sent to the indoor units 40, 50, 60 via the four-way switching valve 22, the gas-side shutoff valve 27, and the gas refrigerant communication tube 72.
The high-pressure gas refrigerant sent to the indoor units 40, 50, 60 exchanges heat with indoor air in the indoor heat exchangers 42, 52, 62 and condenses to high-pressure liquid refrigerant, which then passes through the indoor expansion valves 41, 51, 61 to be pressure-reduced in accordance with the valve opening degrees of the indoor expansion valves 41, 51, 61.
The refrigerant that has passed through the indoor expansion valves 41, 51, 61 is sent to the outdoor unit 20 via the liquid refrigerant communication tube 71 and further pressure-reduced via the liquid-side shutoff valve 26 and the outdoor expansion valve 38, after which the refrigerant flows into the outdoor heat exchanger 23. The low-pressure gas-liquid two-phase refrigerant that has flowed into the outdoor heat exchanger 23 exchanges heat with outdoor air supplied by the outdoor fan 28 and evaporates to low-pressure gas refrigerant, which flows into the accumulator 24 via the four-way switching valve 22. The low-pressure gas refrigerant that has flowed into the accumulator 24 is again drawn into the compressor 21. Because the air conditioning apparatus 10 has no mechanisms for adjusting the pressure of the refrigerant in the gas sides of the indoor heat exchangers 42, 52, 62, the indoor heat exchangers 42, 52, 62 all share a common condensation pressure Pc.
Energy conservation control is performed during the air-heating operation in the air conditioning apparatus 10. The energy conservation control during the air-heating operation is described below on the basis of the flowchart of
First, in step S21, the air-conditioning capability calculation units 47a, 57a, 67a of the indoor-side control devices 47, 57, 67 of the indoor units 40, 50, 60 respectively calculate the current air-conditioning capabilities Q31, Q32, Q33 in the indoor units 40, 50, 60 on the basis of temperature differences ΔTcr1, ΔTcr2, ΔTcr3 which are the temperature differences between the indoor temperatures Tr1, Tr2, Tr3 and the condensation temperature Tc, indoor fan airflow volumes Ga1, Ga2, Ga3 caused by the indoor fans 43, 53, 63, and the degrees of subcooling SC1, SC2, SC3, at that point in time. The calculated air-conditioning capabilities Q31, Q32, Q33 are stored respectively in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67. The air-conditioning capabilities Q31, Q32, Q33 may also be calculated using the condensation temperature Tc instead of the temperature differences ΔTcr1, ΔTcr2, ΔTcr3.
In step S22, the air-conditioning capability calculation units 47a, 57a, 67a respectively calculate displacements ΔQ1, ΔQ2, ΔQ3 of the air-conditioning capabilities in the indoor space on the basis of the indoor temperatures Tr1, Tr2, Tr3 detected respectively by the indoor temperature sensors 46, 56, 66, and the temperature differences ΔT1, ΔT2, ΔT3 with the set temperatures Ts1, Ts2, Ts3 set by a user through a remote controller or the like at the time. The air-conditioning capability calculation units 47a, 57a, 67a then respectively calculate required capabilities Q41, Q42, Q43 by adding the displacements to the air-conditioning capabilities Q31, Q32, Q33. The calculated required capabilities Q41, Q42, Q43 are respectively stored in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67. Though not shown in
Specifically, due to indoor temperature control, the air-conditioning capabilities of the indoor units 40, 50, 60 continue to be maintained respectively between the above-described air-conditioning capabilities Q31, Q32, Q33 and the required capabilities Q41, Q42, Q43. Essentially, the amount of heat exchanged in the indoor heat exchangers 42, 52, 62 is between the air-conditioning capabilities Q31, Q32, Q33 of the indoor units 40, 50, 60 and the required capabilities Q41, Q42, Q43. Therefore, during energy conservation control when sufficient time has elapsed after the start of operation and a nearly steady state has been reached, the air-conditioning capabilities Q31, Q32, Q33 of the indoor units 40, 50, 60 and/or the required capabilities Q41, Q42, Q43 are nearly equivalent to the current amounts of heat exchanged in the indoor heat exchangers 42, 52, 62.
In step S23, a confirmation is made as to whether the airflow-volume set mode in the remote controllers of the indoor fans 43, 53, 63 is the automatic-airflow-volume-control mode or the constant-airflow-volume mode. When the airflow-volume set mode of the indoor fans 43, 53, 63 is the automatic-airflow-volume-control mode, the sequence transitions to step S24, and when the mode is the constant-airflow-volume mode, the sequence transitions to step S25.
In step S24, the required temperature calculation units 47b, 57b, 67b respectively calculate required condensation temperatures Tcr1, Tcr2, Tcr3 of the indoor units 40, 50, 60 on the basis of the required capabilities Q41, Q42, Q43, the airflow volume maximum values GaMAX1, GaMAX2, GaMAX3 (the airflow volumes in “high airflow”) of the indoor fans 43, 53, 63, and degree of subcoolling minimum values SCmin1, SCmin2, SCmin3. The required temperature calculation units 47b, 57b, 67b also respectively calculate condensation temperature differences ΔTc1, ΔTc2, ΔTc3, which are the required condensation temperatures Tcr1, Tcr2, Tcr3 less the condensation temperatures Tc1, Tc2, Tc3 detected by the liquid line temperature sensors 44, 54, 64 at the time. The term “degree of subcooling minimum value SCmin” used herein refers to the minimum value of the range in which the degree of subcooling can be set by adjusting the opening degrees of the indoor expansion valves 41, 51, 61, and the respective values SCmin1, SCmin2, SCmin3 are set according to the model. In the indoor units 40, 50, 60, when the airflow volumes of the indoor fans 43, 53, 63 and/or the degrees of subcooling are brought to the airflow volume maximum values GaMAX1, GaMAX2, GaMAX3 and the degree of subcooling minimum values SCmin1, SCmin2, SCmin3, if they are not currently at the airflow volume maximum values GaMAX1, GaMAX2, GaMAX3 and the degree of subcooling minimum values SCmin1, SCmin2, SCmin3, it is possible to create a state in which greater amounts of heat exchanged than the current amounts are exhibited in the indoor heat exchangers 42, 52, 62. Therefore, an operating state amount involving the airflow volume maximum values GaMAX1, GaMAX2, GaMAX3 and the degree of subcooling minimum values SCmin1, SCmin2, SCmin3 is an operating state amount that can create a state in which greater amounts of heat exchanged than the current amounts are exhibited in the indoor heat exchangers 42, 52, 62. The calculated condensation temperature differences ΔTc1, ΔTc2, ΔTc3 are then stored respectively in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67.
In step S25, the required temperature calculation units 47b, 57b, 67b respectively calculate the required condensation temperatures Tcr1, Tcr2, Tcr3 of the indoor units 40, 50, 60 on the basis of the required capabilities Q41, Q42, Q43, the constant airflow volumes Ga1, Ga2, Ga3 (e.g., the airflow volumes in “medium airflow”) of the indoor fans 43, 53, 63, and the degree of subcooling minimum values SCmin1, SCmin2, SCmin3. The required temperature calculation units 47b, 57b, 67b also respectively calculate the condensation temperature differences ΔTc1, ΔTc2, ΔTc3, which are the required condensation temperatures Tcr1, Tcr2, Tcr3 less the condensation temperatures Tc1, Tc2, Tc3 detected by the liquid line temperature sensors 44, 54, 64 at the time. The calculated condensation temperature differences ΔTc1, ΔTc2, ΔTc3 are stored respectively in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67. In this step S25, the constant airflow volumes Ga1, Ga2, Ga3 are employed instead of the airflow volume maximum values GaMAX1, GaMAX2, GaMAX3, but the purpose of this is to prioritize the airflow volumes set by the user, and the airflow volumes will be recognized as maximum values within the airflow volume range set by the user.
In step S26, the condensation temperature differences ΔTc1, ΔTc2, ΔTc3, which had been stored respectively in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67 in steps S24 and S25, are sent to the outdoor-side control device 37 and stored in the memory 37b of the outdoor-side control device 37. The target value appointing unit 37a of the outdoor-side control device 37 then appoints a maximum condensation temperature difference ΔTcmax, which is the maximum among the condensation temperature differences ΔTc1, ΔTc2, ΔTc3, as the target condensation temperature difference ΔTct. For example, when the condensation temperature differences ΔTc1, ΔTc2, ΔTc3 of the indoor units 40, 50, 60 are 1° C., 0° C., and −2° C., the ΔTcmax is 1° C.
In step S27, the operating capacity of the compressor 21 is controlled on the basis of the target condensation temperature difference ΔTct. Thus, as a result of the operating capacity of the compressor 21 being controlled on the basis of the target condensation temperature difference ΔTct, in the indoor unit (assume the indoor unit 40 in this case) that had calculated the maximum condensation temperature difference ΔTcmax employed as the target condensation temperature difference ΔTct, the indoor fan 43 is adjusted so as to reach the airflow volume maximum value GaMAX1 when set to the automatic-airflow-volume-control mode, and the indoor expansion valve 41 is adjusted so that the degree of subcooling SC in the outlet of the indoor heat exchanger 42 reaches the degree of subcooling minimum value SCmin1.
Air-heating heat exchange functions, which differ for each of the indoor units 40, 50, 60 and take into account the relationships of the air-conditioning (required) capabilities Q31, Q32, Q33 (Q41, Q42, Q43), airflow volumes Ga1, Ga2, Ga3, degrees of subcooling SC1, SC2, SC3, and temperature differences ΔTcr1, ΔTcr2, ΔTcr3 (the temperature difference between the indoor temperature Tr and the condensation temperature Tc) of each of the indoor units 40, 50, 60, are used to calculate the air-conditioning capabilities Q31, Q32, Q33 in step S21 and to calculate the condensation temperature differences ΔTc1, ΔTc2, ΔTc3 in step S24 or S25. These air-heating heat exchange functions are relational expressions associated with the air-conditioning (required) capabilities Q31, Q32, Q33 (Q41, Q42, Q43), airflow volumes Ga1, Ga2, Ga3, degrees of subcooling SC1, SC2, SC3, and temperature differences ΔTcr1, ΔTcr2, ΔTcr3 representing the characteristics of the indoor heat exchangers 42, 52, 62, and these functions are stored respectively in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67 of the indoor units 40, 50, 60. One variable among the air-conditioning (required) capabilities Q31, Q32, Q33 (Q41, Q42, Q43), airflow volumes Ga1, Ga2, Ga3, degrees of subcooling SC1, SC2, SC3, and temperature differences ΔTcr1, ΔTcr2, ΔTcr3 is determined respectively by inputting the other three variables into the air-heating heat exchange functions. The condensation temperature differences ΔTc1, ΔTc2, ΔTc3 can thereby be brought to the proper values with precision, and the target condensation temperature difference ΔTct can be accurately determined.
Therefore, excessive increases of the condensation temperature Tc can be prevented. Therefore, excess and deficiency in the air-conditioning capabilities of the indoor units 40, 50, 60 can be prevented, the optimal states of the indoor units 40, 50, 60 can be achieved quickly and stably, and a greater energy conservation effect can be exhibited.
The operating capacity of the compressor 21 is controlled on the basis of the target condensation temperature difference ΔTct in this flow, but this control is not limited to the target condensation temperature difference ΔTct, the target value appointing unit 37a may appoint the maximum value of the requested condensation temperature Tcr calculated in the indoor units 40, 50, 60 as the target condensation temperature Tct, and the operating capacity of the compressor 21 may be controlled on the basis of the appointed target condensation temperature Tct.
The operation controls described above are performed by the operation control device 80 (more specifically, the indoor-side control devices 47, 57, 67, the outdoor-side control device 37, and the transmission line 80a connecting them) which functions as operation control means for performing normal operations including the air-cooling operation and the air-heating operation.
(2-3) Equalizing Indoor Unit Operating States
Next,
For this description, the indoor units 40, 50, 60 are designated as a single group AA. The indoor-side control devices 47, 57, 67 have the information that the respective indoor units 40, 50, 60 belong to group AA. The indoor units 40, 50, 60 obtain information pertaining to the groups of other indoor units (step S31), whereby the indoor units 40, 50, 60 perform a grouping indicating that the units belong to the same group AA. The indoor-side control devices 47, 57, 67 then obtain information indicating whether the indoor units 40, 50, 60 belonging to the same group AA are thermo-ON or thermo-OFF (step S32).
Next, an assessment made among the indoor units 40, 50, 60 as to whether all of the indoor units 40, 50, 60 belonging to group AA are thermo-ON, all are thermo-OFF, or there are both thermo-ON indoor units and thermo-OFF indoor units (step S33).
When it is assessed in step S33 that all three of the indoor units 40, 50, 60 in group AA are thermo-ON, the indoor-side control devices 47, 57, 67 recognize that there is no need to resolve there are both thermo-ON and thermo-OFF units. In view of this, the indoor units 40, 50, 60 return to step S32 and again obtain the information indicating whether the indoor units 40, 50, 60 are thermo-ON or thermo-OFF with the following timing. The operation of step S33 onward is then performed.
When it is assessed in step S33 that all three of the indoor units 40, 50, 60 in group AA are thermo-OFF, the indoor-side control devices 47, 57, 67 recognize that there is no need to resolve there are both thermo-ON and thermo-OFF units. However, at this time, there are both cases in which all three units in group AA are set to the thermo-ON differential of the initial state, and cases in which the thermo-ON differential of some indoor units is reduced from the initial state by the operation of step S35, described hereinafter. The thermo-ON differential is the temperature difference between the set temperature and the temperature at which an indoor unit in the thermo-OFF state is switched thermo-ON. In view of this, in order to return the thermo-ON differential to the initial state in an indoor unit of which the thermo-ON differential has been reduced from the initial state, the thermo-ON differentials of the indoor units 40, 50, 60 in group AA are reset (step S36). The indoor units 40, 50, 60 then return to step S32 and again obtain the information indicating whether the indoor units 40, 50, 60 are thermo-ON or thermo-OFF. The operation of step S33 onward is then performed.
When it is assessed in step S33 that some of the three indoor units 40, 50, 60 in group AA are thermo-OFF, the indoor-side control devices 47, 57, 67 of the indoor units 40, 50, 60 all recognize that there are both thermo-ON and thermo-OFF units. Therefore, the indoor-side control devices 47, 57, 67 of the indoor units 40, 50, 60 advance to the next step S34, and from the thermo-ON and thermo-OFF information stored in the memories 47c, 57c, 67c of the indoor-side control devices 47, 57, 67, the control devices assess whether or not there are indoor units within group AA that have continued to be thermo-ON for ten minutes or longer, and also indoor units within group AA that have continued to be thermo-OFF for ten minutes or longer. In this step S34, a continuation of ten minutes is assessed, but the continuation time is set as appropriate. For example, when the indoor unit 40 has continued to he thermo-ON for ten minutes or longer and the indoor units 50, 60 have continued to be thermo-OFF for ten minutes or longer, the assessment condition of step S34 is satisfied, and the sequence therefore advances to the next step S35. As another example, when the indoor unit 40 has continued to be thermo-ON for ten minutes or longer but the indoor units 50, 60 have repeated thermo-ON and thermo-OFF and have only continued thermo-OFF for less than ten minutes, the assessment condition of step S34, is not satisfied, the sequence therefore returns to step S32, and the operation of step S32 onward is repeated.
In step S35, an operation is performed for reducing the thermo-ON differential by 0.2° C. in indoor units continuing to be thermo-OFF. The differentially is provisionally reduced by 0.2° C. in this step S35, but the value by which the reduction is made is set as appropriate. In the example described above, the thermo-ON differentials of the indoor units 40, 50, 60 are reduced by 0.2° C. because the indoor units 50, 60 have continued to be thermo-OFF for ten minutes or longer. In another case, the thermo-ON differentials of the indoor units 40, 50, 60 are reduced by 0° C. even when, e.g., the indoor unit 50 has continued to be thermo-OFF for ten minutes or longer but the time duration of the indoor unit 60 being thermo-OFF is less than ten minutes. After the operation of this step S35, the sequence returns to step S32 and the operation of step S32 onward is repeated.
At time t0 shown in
Due to the thermo-ON differentials decreasing at time t1, the temperature difference between curve C2 and the set value setting temperature is greater than the thermo-ON differentials after the decrease, and the indoor unit 50 is therefore thermo-ON.
The time duration between time t1 and time t2 is an interval following time t1 and lasting until the procedure of step S32 onward is performed. At time t2, there are both thermo-ON indoor units 40, 50 and a thermo-OFF indoor unit 60, the sequence therefore advances to step S35, and the thermo-ON differentials of the indoor units 40, 50, 60 are further reduced by 0.2° C. As a result, due to the thermo-ON differentials decreasing at time t2, the temperature difference between curve C3 and the set value setting temperature is greater than the thermo-ON differentials after the decrease, and the indoor unit 60 is therefore thermo-ON.
(3) Characteristics
(3-1)
As described above, the indoor units 40, 50, 60 of the air conditioning apparatus 10 are installed in one room 1 (an example of the same indoor space). The indoor units 40, 50, 60 include respective indoor heat exchangers 42, 52, 62 (an example of the usage-side heat exchangers), and the indoor units are configured to be capable of setting the set temperatures individually. The indoor-side control devices 47, 57, 67 (an example of the control devices) cause temperature control of the room 1 to be performed in each of the indoor units 40, 50, 60, using a thermo-ON condition set in advance in accordance with the set temperature. When the indoor units 40, 50, 60 include both those that are thermo-ON and those that are thermo-OFF and a predetermined condition is satisfied, the indoor-side control devices 47, 57, 67 reduce the thermo-ON differentials of the indoor units 40, 50, 60 that are thermo-OFF (an example of relaxing the thermo-ON condition).
At times t1 and t2 at which there are both thermo-ON units and thermo-OFF units among the three indoor units 40, 50, 60, the thermo-ON condition is relaxed, whereby the number of thermo-ON indoor units can be quickly increased from one to two and also from two to three to increase the number of indoor heat exchangers 42, 52, 62 that are exchanging heat with the refrigerant circulating in the outdoor heat exchanger 23 (an example of the heat-source-side heat exchanger). As a result, there are more indoor units 40, 50, 60 that are thermo-ON, whereby heat exchange can be balanced with the apparent area of all the indoor heat exchangers 42, 52, 62 together (the sum of the area of the thermo-ON indoor heat exchangers 42, 52, 62) having increased, and the differential pressure between the evaporation pressure and the condensation pressure of the air conditioning system can be reduced to improve the efficiency of the entire air conditioning system.
The predetermined condition for the indoor-side control devices 47, 57, 67 is that among the indoor units 40, 50, 60 there are units that have continued to be thermo-ON for ten minutes (an example of the first elapsed time) or longer, and there are also units that have continued to be thermo-OFF for ten minutes (an example of the second elapsed time) or longer. It is possible to prevent a relaxing of the thermo-ON condition due to a temporary state in which indoor units that should he thermo-ON have continued to not he thermo-ON for ten minutes, or a temporary state in which indoor units that should be thermo-OFF have continued to not be thermo-OFF for ten minutes. Due to the control being configured in this manner, efficiency can be improved while imbalance of the temperature in the same indoor space is suppressed.
In the method for controlling the air conditioning system shown in
(3-2)
As shown in
(3-3)
The indoor-side control devices 47, 57, 67 of the operation control device 80, through the required temperature calculation units 47b, 57b, 67b, calculate, each indoor unite, the required evaporation temperatures or the required condensation temperatures of the indoor heat exchangers 42, 52, 62. The outdoor-side control device 37 of the operation control device 80 appoints a target evaporation temperature on the basis of the minimum value among the required evaporation temperatures of the indoor units 40, 50, 60 calculated in the required temperature calculation units 47b, 57b, 67b. Alternatively, the outdoor-side control device 37 of the operation control device 80, through the target value appointing unit 37a, appoints a target condensation temperature on the basis of the maximum value among the required condensation temperatures of the indoor units 40, 50, 60 calculated in the required temperature calculation units 47b, 57b, 67b. A target evaporation temperature or a target condensation temperature is thereby appointed for the outdoor unit 20 in response to the highest requirement of air-conditioning capability from among the indoor units 40, 50, 60, whereby a target evaporation temperature or target condensation temperature complying with the air-conditioning capability requirements of all the indoor units 40, 50, 60 can be appointed and efficiency can be improved while preventing deficiencies in air-conditioning capability in some indoor units.
(3-4)
Because the indoor-side control device 47 of the indoor unit 40, which is the base unit described above, uses the above formulas (1) and (2), rated capacities (an example of the degree of influence on the thermal environment of the indoor space) are derived from the differences between the set temperatures and the detected temperatures (an example of the control temperatures) of the respective indoor temperature sensors 46, 56, 66 of the indoor units 40, 50, 60. In other words, a weighted average value, which is weighted by the rated capacities, is used as the representative temperature related value. Emphasis can thereby be placed on the indoor unit that has the greatest rated capacity and the greatest degree of influence on the thermal environment of the indoor space, and the degree of influence of each of the indoor units 40, 50, 60 on the indoor environment can be reflected.
(3-5)
The thermo-ON condition is a condition that the indoor units 40, 50, 60 be thermo-ON when there is a predetermined temperature difference (the thermo-ON differential) between the set temperature and the temperatures detected by the indoor temperature sensors 46, 56, 66 (an example of the control temperatures), and the indoor-side control devices relax the thermo-ON condition by reducing the thermo-ON differential (an example of reducing the predetermined temperature difference of the thermo-ON condition). Relaxing of the thermo-ON condition can thus be achieved by a simple operation of altering the thermo-ON differential, and control of an air conditioning system that readily turns thermo-ON can be achieved in a simple manner.
(3-6)
The indoor units 40, 50, 60 comprise respective indoor fans 43, 53, 63 (an example of the air blowers) of which the airflow volumes sent to the indoor heat exchangers 42, 52, 62 can be adjusted. The indoor-side control devices 47, 57, 67 adjust the indoor fans 43, 53, 63 for each indoor unit, reduce the airflow volumes if the air-conditioning capabilities are excessive, and increase the airflow volumes if the air-conditioning capabilities are insufficient. Through this manner of control, the indoor-side control devices 47, 57, 67 can autonomously adjust the air-conditioning capability of each indoor unit via the airflow volumes of the indoor fans 43, 53, 63, and can autonomously optimize the air-conditioning capability. The number of thermo-ON indoor units is increased by relaxing the thermo-ON condition, and although there are cases of excessive air-conditioning capability leading to temporary instances of poor efficiency, this autonomous optimization takes effect in these cases as well, suppressing the loss of efficiency.
(3-7)
The indoor units 40, 50, 60 comprise respective indoor expansion valves 41, 51, 61 (an example of the expansion mechanisms) capable of adjusting the degrees of superheat or the degrees of subcooling in the outlet sides of the indoor heat exchangers 42, 52, 62. The indoor-side control devices 47, 57, 67 adjust the opening degrees of the indoor expansion valves 41, 51, 61 in each indoor unit, reduce the degrees of superheat or the degrees of subcooling if the air-conditioning capabilities are excessive, and increase the degrees of superheat or the degrees of subcooling if the air-conditioning capabilities are insufficient. The air-conditioning capability can be autonomously optimized in each indoor unit by adjusting the opening degrees of the indoor expansion valves 41, 51, 61 in this manner. The number of thermo-ON indoor units is increased by relaxing the thermo-ON condition, and although there are cases of excessive air-conditioning capability leading to temporary instances of poor efficiency, this autonomous optimization takes effect in these cases as well, suppressing the loss of efficiency.
(4) Modifications
(4-1) Modification 1A
In the above embodiment, the indoor-side control devices 47, 57, 67, or the operation control device 80 including the indoor-side control devices 47, 57, 67 and the outdoor-side control device 37, were given as examples of control devices, but examples of control devices are not limited thereto, and the control devices may be centralized controllers which acquire data from the outdoor unit 20 and the indoor units 40, 50, 60, and which provide data to the outdoor unit 20 and the indoor units 40, 50, 60. The entire air conditioning system is easily harmonized by the unifying management of the centralized controllers.
[Patent Literature 1] Japanese Laid-open Patent Application No. 2011-257126
| Number | Date | Country | Kind |
|---|---|---|---|
| 2013-204145 | Sep 2013 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2014/075601 | 9/26/2014 | WO | 00 |
