JP5528512B2 - Control device, control method and program - Google Patents

Control device, control method and program Download PDF

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JP5528512B2
JP5528512B2 JP2012173459A JP2012173459A JP5528512B2 JP 5528512 B2 JP5528512 B2 JP 5528512B2 JP 2012173459 A JP2012173459 A JP 2012173459A JP 2012173459 A JP2012173459 A JP 2012173459A JP 5528512 B2 JP5528512 B2 JP 5528512B2
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temperature
unit
temperature difference
set
indoor
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JP2012233689A (en
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恵美 竹田
史武 畝崎
正樹 豊島
直道 田村
博司 堤
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三菱電機株式会社
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Description

  The present invention relates to a control device, a control method, and a program for controlling an air conditioner including an outdoor unit connected via a refrigerant circuit and a plurality of indoor units.

  Conventionally, a refrigerant circuit configured by connecting a heat source unit and a plurality of utilization units, a capacity control means for controlling the air conditioning capacity so that the physical quantity of the refrigerant becomes a target value, and a target value of the capacity control means are changed. There has been proposed an air conditioner including a target value adjusting means (see, for example, Patent Document 1). This air conditioner variably controls the target value in accordance with the air conditioning load characteristics of the building.

  If the target value of the refrigerant temperature is changed based on the air conditioning load of the building, it is possible to operate with the air conditioning capacity that matches the air conditioning load characteristic of the building, and to prevent excessive capacity in the intermediate period. Thereby, the operating efficiency of an air conditioning apparatus improves and economical efficiency improves.

  In addition, the compressor capacity is controlled based on the temperature difference between the set temperature and the detected temperature, the rated capacity of the indoor unit, the capacity setting value of the indoor heat exchanger, the load constant, etc. A harmony device has been proposed (see, for example, Patent Document 2).

Japanese Patent No. 4032634 Japanese Patent No. 4043255

  In the air conditioning apparatus described in Patent Document 2, the control target value can be determined at the most efficient point as long as the air conditioning load characteristic can be accurately obtained. However, in actuality, the amount of heat generated in the building constantly changes depending on the number of people in the room, the lighting, and the usage status of the OA equipment, and the heat capacity and the housing temperature of the room also vary. For this reason, it is extremely difficult to calculate the heat load and necessary capacity in accordance with various air conditioning environments and to accurately obtain the air conditioning load characteristics. As a result, even if the air conditioning apparatus is actually operated, comfort and efficiency cannot always be improved.

  For example, the change in room temperature is slow when the capacity of the air conditioner is small relative to the required capacity and heat capacity. This slowness gives the user dissatisfaction with “not getting cold” or “not getting warm”. On the other hand, if the capacity of the air conditioner is too large relative to the required capacity or heat capacity, the room temperature changes rapidly, the refrigeration cycle is not stabilized, and the efficiency deteriorates.

  In addition, there are various combinations of air conditioners that connect an outdoor unit and a plurality of indoor units. For this reason, when such an air conditioner is controlled using a load constant or the like, it becomes difficult to cope with a load constant that is different for each air conditioning system, so this control method lacks versatility.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a control device, a control method, and a program capable of reducing power consumption while ensuring comfort.

In order to achieve the above object, a control device according to the present invention includes an outdoor unit connected via a refrigerant circuit, and a plurality of indoor units that switch between thermo-on and thermo-off based on a temperature difference between a set temperature and a room temperature. It is a control apparatus which controls an air conditioning apparatus provided with. In this control system, command generation unit, among the plurality of indoor units, the indoor unit temperature difference is maximum is set as the master unit is a heat load up to the indoor unit, a new temperature difference is the largest When a new indoor unit is selected as a candidate for the master unit and the master unit is set for the first time, or when an indoor unit already set as the master unit is thermo-off, or the temperature difference in the candidate for the master unit exceeds a predetermined value. In this case, the master unit candidate is set as a new master unit, and a command to the compressor of the outdoor unit is generated according to the temperature difference in the master unit.

  According to this invention, the indoor unit with the maximum heat load is used as a reference for control. Thereby, since the frequency of a compressor can be reduced to the minimum necessary, comfort is ensured and power consumption can be reduced.

1 is a floor plan view of a building to which an air conditioner according to Embodiment 1 of the present invention is applied. It is a block diagram which shows the structure of the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a circuit diagram of the refrigerant circuit of the air conditioning apparatus which concerns on Embodiment 1 of this invention. FIG. 3 is a thermo-on / thermo-off control diagram in the air-conditioning apparatus of FIG. 2. It is a graph which shows the relationship between the value which totaled the rated capacity of the indoor unit of a thermo-on state, and the maximum frequency of a compressor. It is a table which shows the list of the information which a controller has at the time of a setting completion. It is a flowchart of an energy saving mode control process. It is a flowchart of the subroutine of the temperature difference determination process of FIG. It is a flowchart of the subroutine of the maximum frequency determination process of FIG. FIG. 10A is a graph showing the relationship between the temperature difference and the maximum frequency in the normal mode. FIG. 10B is a graph showing the relationship between the temperature difference and the maximum frequency in the energy saving mode. It is a graph which shows the relationship between the maximum frequency of a compressor, and a control signal. It is a flowchart of the energy-saving mode control process which concerns on Embodiment 2 of this invention. It is a flowchart of the subroutine of the control signal determination process of FIG. It is a graph which shows the relationship between a temperature difference and a control signal. It is a flowchart of the energy-saving mode control process which concerns on Embodiment 3 of this invention. It is a flowchart of the subroutine of the target evaporation temperature determination process of FIG. FIG. 17A is a graph showing the relationship between the temperature difference and the target evaporation temperature in the normal mode. FIG. 17B is a graph showing the relationship between the temperature difference and the target evaporation temperature in the energy saving mode. It is a flowchart of the energy-saving mode control process which concerns on Embodiment 3 of this invention. It is a flowchart of the subroutine of the target condensation temperature determination process of FIG. FIG. 20A is a graph showing the relationship between the temperature difference and the target condensation temperature in the normal mode. FIG. 20B is a graph showing the relationship between the temperature difference and the target condensation temperature in the energy saving mode. It is a floor top view of the building where the air conditioning apparatus which concerns on Embodiment 4 of this invention is applied. It is a side view of an office room. It is a block diagram which shows the structure of the air conditioning apparatus which concerns on Embodiment 4 of this invention.

  Embodiments of the present invention will be described in detail with reference to the drawings.

Embodiment 1 FIG.
First, a first embodiment of the present invention will be described. In this embodiment, a multi-room air conditioner that performs air conditioning of a plurality of rooms will be described.

  FIG. 1 shows a floor plan view of a building to which an air conditioner according to this embodiment is applied. As shown in FIG. 1, an office room A, a meeting room B, a meeting room C, and an office room D are provided in this building. On the ceiling of the office room A, indoor units 1 to 8 are installed. An indoor unit 9 is installed on the ceiling of the conference room B, an indoor unit 10 is installed on the ceiling of the conference room C, and an indoor unit 11 is installed on the ceiling of the office room D.

  FIG. 2 shows the configuration of air-conditioning apparatus 100 according to Embodiment 1 of the present invention. As shown in FIG. 2, the air conditioner 100 includes three outdoor units 51, 52, and 53. Indoor units 1 to 4 are connected to the outdoor unit 51. The indoor units 5 to 8 are connected to the outdoor unit 52. Furthermore, the indoor units 9 to 11 are connected to the outdoor unit 53.

  The outdoor units 51 to 53 and the indoor units 1 to 11 are connected by the transmission line 30 and the liquid side main pipe 104, the liquid side branch pipe 105, the gas side branch pipe 108, and the gas side main pipe 109. Yes. The outdoor units 51 to 53, the controller 201, and the power feeder 203 are also connected by the transmission line 30.

  A remote controller 204 is connected to the indoor units 1 to 4 via the transmission line 30. A remote controller 205 is connected to the indoor units 5, 6, 7, and 8 via the transmission line 30. A remote controller 206 is connected to the indoor unit 9, a remote controller 207 is connected to the indoor unit 10, and a remote controller 208 is connected to the indoor unit 11. By operating the remote controllers 204 to 208, the operation / stop of the indoor units 1 to 11, the set temperature, the wind direction, the wind speed, and the like can be set.

  The controller 201 includes a CPU and a memory. When the CPU executes a program stored in the memory, the controller 201 performs overall control of the entire air conditioning apparatus 100.

  FIG. 3 shows a refrigerant circuit of air-conditioning apparatus 100 according to Embodiment 1 of the present invention. Although FIG. 3 shows the system of the outdoor unit 51, the system of the outdoor unit 52 and the outdoor unit 53 has the same configuration as that shown in FIG. Four indoor units 1 to 4 are connected to the outdoor unit 51, but all the indoor units 1 to 4 have the same configuration. For this reason, in FIG. 3, the indoor units 3 and 4 are not illustrated.

  The outdoor unit 51 is provided with an inverter-driven variable capacity compressor 101, a cooling / heating switching four-way valve 102, an outdoor heat exchanger 103, and an accumulator 110.

  An expansion valve 106 and an indoor heat exchanger 107 are provided in the indoor units 1 to 4. In the indoor units 1 to 4, a refrigerant circuit is formed by connecting them. The expansion valve 106 can perform pulse control of the valve opening using a stepping motor. As described above, the outdoor unit 51 and the indoor units 1 to 4 are connected by the liquid side main pipe 104, the liquid side branch pipe 105, the gas side main pipe 109, and the gas side branch pipe 108.

  In the compressor 101, a discharge pressure sensor 111 is provided on the discharge side, and a suction pressure sensor 112 is provided on the suction side. On the other hand, the indoor units 1 to 4 are provided with a liquid pipe temperature sensor 114 and a gas pipe temperature sensor 115.

  The outdoor unit 51 is provided with an outdoor blower (not shown) for flowing air to the outdoor heat exchanger 103. An outdoor temperature sensor 113 is provided on the air suction side of the outdoor heat exchanger 103. Further, the outdoor unit 51 is provided with an outdoor control box 117. A controller for controlling the outdoor unit 51 is housed in the outdoor control box 117.

  Each of the indoor units 1 to 4 is provided with an indoor blower (not shown). Air is sucked from the air-conditioning area by the indoor blower, and the air is passed through the indoor heat exchanger 107 and is blown to the air-conditioning area. An intake air temperature sensor 116 is provided on the air intake side of the indoor heat exchanger 107. The indoor units 1 to 4 are provided with an indoor control box 118. A controller for controlling the indoor units 1 to 4 is housed in the outdoor control box 118.

  Next, operation | movement of the air conditioning apparatus 100 which concerns on this embodiment is demonstrated.

(Cooling operation)
First, the refrigeration cycle of the cooling operation will be described with reference to FIG. The refrigerant discharged from the compressor 101 flows from the four-way valve 102 to the outdoor heat exchanger 103, exchanges heat with air, condenses and liquefies, and branches from the liquid side main pipe 104 to the liquid side branch pipe 105. The refrigerant that has flowed to the indoor heat exchanger 107 evaporates by receiving heat from the air, and then passes through the gas side main pipe 109, the four-way valve 102, and the accumulator 110 from the gas side branch pipe 108 and is again sucked into the compressor 101. .

(Heating operation)
Next, a refrigeration cycle for heating operation will be described. The four-way valve 102 is switched during heating. The refrigerant discharged from the compressor 101 branches from the gas side main pipe 109 to the gas side branch pipe 108, flows to the indoor heat exchanger 107, dissipates heat to the air, condenses and liquefies, and expands on the liquid side branch pipe 105. The pressure is reduced by the valve 106. The refrigerant that has become low pressure through the expansion valve 106 flows through the outdoor heat exchanger 103, obtains heat from the air, evaporates, passes through the four-way valve 102 and the accumulator 110, and is sucked into the compressor 101 again.

(Capacity adjustment operation of refrigeration cycle)
Here, the temperature of the intake air temperature sensor 116 is T, and the set temperature is T0. Further, the temperature difference ΔT (° C.) is defined as the following equation (1) during cooling, and the temperature difference ΔT (° C.) is defined as the following equation (2) during heating.
During cooling ΔT = T−T0 (1)
During heating ΔT = T0−T (2)
As shown in FIG. 4, each of the indoor units 1 to 4 has a temperature difference ΔT (° C.) between the temperature T (° C.) of the intake air temperature sensor 116 and the set temperature T 0 (° C.) increased from + T 1 (° C.). The expansion valve 106 is opened and the refrigerant flows to the indoor heat exchanger 107. This operation is called thermo-on. Further, each of the indoor units 1 to 4 closes the expansion valve 106 to reduce or stop the inflow of the refrigerant when the temperature difference ΔT (° C.) becomes −T1 (° C.) or less. This operation is called thermo-off.

  The outdoor unit 51 operates the compressor 101 when one of the connected indoor units 1 to 4 is in the thermo-on state, and sets the frequency to 0 Hz when all of the indoor units 1 to 4 are in the thermo-off state, and stops the compressor 101.

  In the case of cooling, the outdoor unit 51 sets the frequency of the compressor 101 so that the refrigerant saturation temperature (evaporation temperature) obtained from the pressure value (low pressure) of the suction pressure sensor 112 matches the target evaporation temperature ET. Control. In the case of heating, the outdoor unit 51 sets the frequency of the compressor 101 so that the refrigerant saturation temperature (condensation temperature) obtained from the pressure value (high pressure) of the discharge pressure sensor 111 matches the target condensation temperature CT. Control.

  FIG. 5 shows the relationship between the sum of the rated capacities of the indoor units in the thermo-on state and the maximum frequency of the compressor 101. As shown in FIG. 5, the limit value F1 (Hz) of the maximum frequency of the compressor 101 is a value obtained by summing the rated capacities of the indoor units in the thermo-on state among the indoor units 1 to 4 connected to the outdoor unit 51 ( It is set according to the total rated capacity). In the normal mode, the compressor 101 is operated at a maximum frequency F1 (Hz) or less as shown in FIG. The maximum frequency F1 (Hz) is limited in proportion to the product of the number of indoor units thermo-on and the capacity code.

  An operation when the frequency of the compressor 101 is changed will be described.

  For example, when the frequency of the compressor 101 is decreased, the refrigerant flow rate is decreased, the pressure value (low pressure) of the suction pressure sensor 112 is increased, and the saturation temperature (evaporation temperature) of the refrigerant at low pressure is increased. In addition, the pressure value (high pressure) of the discharge pressure sensor 111 decreases, and the saturation temperature (condensation temperature) of the refrigerant at high pressure decreases. At this time, the amount of heat exchange between the indoor heat exchanger 107 and air (hereinafter referred to as capacity) decreases. When the frequency of the compressor 101 is decreased to reduce the pressure difference between the high pressure and the low pressure, the ratio of the capacity to the input of the compressor 101 (COP; coefficient of performance) is increased and the operation becomes efficient. As a result, the power consumption of the entire air conditioner 100 can be reduced.

(Controller setting)
FIG. 6 shows a list of information that the controller 201 has when setting is completed. Unit addresses of the outdoor units 51 to 53 and the indoor units 1 to 11 are set in advance by a dip switch or the like of the device at the time of construction. In the table shown in FIG. 6, the unit addresses of the outdoor units 51 to 53 are set to 51 to 53, and the unit addresses of the indoor units 1 to 11 are set to 1 to 11.

  The controller 201 communicates with the outdoor units 51 to 53 and the indoor units 1 to 11 to confirm the presence / absence of devices and acquire the connection relationship between the outdoor units 51 to 53 and the indoor units 1 to 11. And an administrator, a user, etc. select either the normal mode or the energy-saving mode for each system. In the table of FIG. 6, the energy saving mode is selected in the system of the outdoor unit 51.

  The remote controllers 204 to 208 may be able to select and execute a control mode. When a plurality of remote controllers are installed as in the system of the outdoor unit 53, the control mode selected by the latest operation input may be validated.

(Fig. 7: Control processing when energy saving mode is selected)
FIG. 7 shows an energy saving mode control process executed when the energy saving mode is selected.

  As shown in FIG. 7, first, the controller 201 sets an initial value of the maximum frequency Fmax (Hz) of the compressor 101 (step S1). Here, F1 (Hz) which is the same as the maximum frequency during operation in the normal mode is set as an initial value.

  Subsequently, the controller 201 determines whether or not the compressor 101 of the outdoor unit J (J = 51) to be controlled is operating (step S2). If any of the connected indoor units 1 to 4 is thermo-ON, the outdoor unit 51 is in operation, and this determination is affirmed (step S2; Yes).

  Only when the compressor 101 is in operation (thermo-on) (step S2; Yes), the controller 201 executes a temperature difference determination subroutine that detects the room temperature and the set temperature and determines the temperature difference ΔT (° C.). (Step S3). Details of this subroutine will be described later.

  Subsequently, the controller 201 executes a subroutine of maximum frequency determination processing for determining the maximum frequency Fmax (Hz) based on the temperature difference ΔT (step S4). Details of this subroutine will also be described later.

  After execution of step S4 or when the compressor 101 is not operating (step S2; No), the controller 201 transmits a control command including the maximum frequency Fmax (Hz) to the compressor 101 (step S5).

  Subsequently, the controller 201 determines whether or not an energy saving control stop command has been input (step S6). If the energy saving control stop command is not input (step S6; No), the controller 201 waits for one minute (step S7) and returns to step S2.

  As described above, unless a stop command for energy saving control is input (step S6; No), the controller 201 repeats steps S2, S3, S4, S5, S6, and S7 at intervals of one minute. When the energy saving control stop command is input (step S6; Yes), the controller 201 returns the maximum frequency Fmax (Hz) to F1 (Hz) (step S8), and outputs a control command including the maximum frequency Fmax (Hz). The data is transmitted to the compressor 101 (step S9), and the process is terminated.

  In this way, the controller 201 obtains the maximum frequency Fmax (Hz) and transmits a control command including the obtained maximum frequency Fmax (Hz) to the outdoor unit 51. By incorporating a program for energy-saving mode control processing into the controller 201 connected to the outdoor units 1 to 4, the control method according to this embodiment can be applied to the existing outdoor units 1 to 4. The application range of energy saving mode can be expanded.

  Further, an outdoor control box 117 of the outdoor units 51 to 53 incorporates an energy saving mode control processing program, notifies the outdoor unit 51 from the controller 201 that the energy saving mode has been set, and receives the energy saving control command. The maximum frequency Fmax (Hz) may be obtained from the box 117 to control the energy saving mode. By incorporating the energy saving mode control process in the outdoor control box 117, the controller 201 can be reduced in size, and the controller 201 can be manufactured at low cost.

  Further, the energy saving mode may be set by the remote controllers 204 to 208. In this case, the fact that the energy saving mode is set is directly notified to the outdoor units 51 to 53 of the system where the remote controller is installed. Alternatively, notification may be made via the controller 201. The remote controllers 204 to 208 are provided with an energy saving mode setting function, thereby improving user convenience.

(Temperature difference determination processing)
The subroutine for determining the temperature difference ΔT (° C.) in step S3 in FIG. 7 will be described in more detail. FIG. 8 shows a flowchart of the subroutine of the temperature difference determination process in step S3.

  As shown in FIG. 8, the controller 201 first selects the outdoor unit J to be controlled (step S11). Here, for example, the outdoor unit 51 is selected as the control target.

  Subsequently, the controller 201 initializes the value of ΔTmax (° C.) to −99 (a value sufficiently smaller than ΔT) (step S12).

  Subsequently, the controller 201 selects the indoor unit I in order from the indoor units 1 to 4 connected to the outdoor unit 51 (step S13). Here, the indoor unit 1 (I = 1) is selected first. Subsequently, the controller 201 determines whether or not the indoor unit I (I = 1) is in a thermo-on state (step S14).

  If it is a thermo-on state (step S14; Yes), the controller 201 receives the temperature (suction air temperature T (° C.)) and the set temperature T0 (° C.) of the suction air temperature sensor 116 from the indoor unit I (step S15). .

  Subsequently, the controller 201 calculates a temperature difference ΔT (° C.) between the intake air temperature T (° C.) and the set temperature T0 (° C.) using the above formula (1) or formula (2) (step S16).

  Subsequently, the controller 201 determines whether or not the temperature difference ΔT (° C.) of the indoor unit I (I = 1) is larger than ΔTmax (° C.) (step S17). Only when the temperature difference ΔT (° C.) is larger than ΔTmax (° C.) (step S17; Yes), the controller 201 sets the indoor unit I (I = 1) as the master unit candidate Ik = I (I = 1) and ΔTmax. The value of temperature difference ΔT (° C.) is substituted for (° C.) (step S18).

  After execution of step S18 or when the temperature difference ΔT (° C.) is equal to or less than ΔTmax (° C.) (step S17; No), the controller 201 completes calculation of the temperature difference ΔT (° C.) for all the indoor units 1 to 11. It is determined whether or not (step S19). Here, since the indoor unit 1 has only been completed, the determination is negative (step S19; No), and the controller 201 selects another indoor unit (step S20). After executing step S20, the controller 201 returns to step S14.

Thereafter, steps S14 to S20 are repeated for the indoor unit I (I = 2 to 4) in the same manner as the indoor unit 1, and when all the indoor units are completed (step S19; Yes), the controller 201 determines the master unit I 0 . The process proceeds (steps S21 to S26).

If; (Yes step S21), and or base unit I 0 was indoor unit is in the thermo-off in the determination processing of the master unit I 0, when setting the first time base unit I 0 (step S22; Yes), or ΔTmax If There is at least 1 ° C. (step S23; Yes), the controller 201 sets the base unit candidates Ik to the new master unit I 0 (step S24). In other cases (steps S21, S22, S23; No), the parent device I 0 is not changed. Here, the initial setting of the parent device I 0 means that the repetitive steps (steps S2 to S7) in FIG. 7 are the first time.

Subsequently, the controller 201 receives the intake air temperature T (° C.) and the set temperature T 0 (° C.) of the parent device I 0 (indoor unit I 0 ) (step S25), and the temperature difference ΔT (° C.) of the parent device I 0. ) Is determined by calculation using the above formula (1) or formula (2) (step S26). The temperature difference ΔT (° C.) of the parent device I 0 is used when determining the maximum frequency Fmax (Hz) in step S4 of FIG. As described above, the compressor 101 can reduce the frequency to the minimum necessary by setting the indoor unit having the maximum temperature difference ΔT (° C.) and the maximum heat load as a base unit. As a result, the power consumption of the entire air conditioner 100 can be reduced.

Further, the determination of the temperature difference ΔT (° C.) may be obtained by the following calculation methods (1) to (3). In this case, the amount of calculation is further reduced and control becomes easier.
(1) The average of all the differences between the intake air temperature T (° C.) and the set temperature T 0 (° C.) of all indoor units in the thermo-on state is obtained as the temperature difference ΔT (° C.).
(2) A temperature difference ΔT (° C.) is obtained by weighted averaging the difference between the intake air temperature T (° C.) and the set temperature T 0 (° C.) with the rated capacity of the indoor unit in the thermo-on state.
(3) Among the indoor units in the thermo-on state, the maximum difference between the intake air temperature T (° C.) and the set temperature T 0 (° C.) is defined as a temperature difference ΔT (° C.).

(Maximum frequency determination processing)
Next, the maximum frequency determination process subroutine of step S4 in FIG. 7 will be described. FIG. 9 shows a flowchart of a subroutine of maximum frequency determination processing. 10A and 10B show the relationship between the temperature difference ΔT (° C.) in the parent machine and the maximum frequency Fmax (Hz) of the compressor 101.

  As shown in FIG. 10A, in the normal mode, the maximum frequency Fmax of the compressor 101 is constant at F1 (Hz) regardless of the temperature difference ΔT (° C.). On the other hand, as shown in FIG. 10 (B), in the energy saving mode, the maximum frequency when the temperature difference ΔT (° C.) of the compressor 101 is 0 (° C.) or less is F0 (Hz) smaller than F1 (Hz). ). F0 (Hz) is, for example, 20 (Hz). Then, when + T2 (° C.) (for example, 1.0 (° C.)) higher than + T1 (° C.) is set and the temperature difference ΔT (° C.) becomes + T2 (° C.) or more, the maximum frequency is set to F1 (Hz). .

  In the range where the temperature difference ΔT is larger than 0 (° C.) and lower than + T2 (° C.), the maximum frequency Fmax (Hz) is proportional to the temperature difference ΔT (° C.) between F0 (Hz) and F1 (Hz). Value. In this subroutine, F0 (Hz), F1 (Hz), and + T2 (° C.) are determined.

  As shown in FIG. 9, first, the controller 201 determines a frequency F0 (Hz) when the temperature difference ΔT (° C.) is 0 (° C.) or less (step S31). The maximum frequency F0 (Hz) is set based on the specifications of the compressor 101 and the like.

  Subsequently, the controller 201 receives the rated capacity total value of the indoor unit that is thermo-ON from the indoor unit or the outdoor unit (step S32). Subsequently, the controller 201 determines the frequency F1 (Hz) corresponding to the total rated capacity based on the relationship as shown in FIG. 5 (step S33).

Subsequently, the controller 201 determines the maximum frequency Fmax (Hz) based on the temperature difference ΔT (° C.) (step S34). Here, when the temperature difference ΔT (° C.) is equal to or greater than + T2 (° C.), the maximum frequency Fmax (Hz) is F1 (Hz), and the temperature difference ΔT (° C.) of the parent device I 0 is 0 (° C.). Between + T2 (° C.), as shown in FIG. 10B, the maximum frequency Fmax (Hz) is proportional to the straight line from F0 (Hz) to F1 (Hz), and the temperature difference ΔT is 0 (° C.). In this case, the maximum frequency Fmax is F0 (Hz).

  Subsequently, the controller 201 outputs a control command including the maximum frequency Fmax (Hz) to the outdoor unit J (step S35). In the case of cooling, the outdoor unit J controls the frequency of the compressor 101 so that the saturation temperature (evaporation temperature) of the refrigerant obtained from the pressure value (low pressure) of the suction pressure sensor 112 matches the target evaporation temperature ET. When a command including the maximum frequency Fmax (Hz) is received, the frequency is controlled so as not to exceed the maximum frequency Fmax (Hz). Similarly to the heating, the controller 201 controls the frequency of the compressor 101 so that the refrigerant condensing temperature matches the target condensing temperature CT. When receiving a control command including the maximum frequency Fmax (Hz), the controller 201 The frequency is controlled so as not to exceed the frequency Fmax (Hz).

  As shown in FIG. 4, the indoor units 1 to 4 repeat the thermo-on and the thermo-off with the temperature difference ΔT (° C.) as the boundary between −T 1 (° C.) and + T 1 (° C.). Usually varies between −T1 (° C.) and + T1 (° C.). By setting + T2 (° C.) to a value larger than + T1 (° C.), the maximum frequency Fmax (Hz) is always controlled at a frequency lower than F1 (Hz) in normal control, and the differential pressure between the high pressure and the low pressure is It becomes smaller and the efficiency of the refrigeration cycle improves. During cooling, if the temperature of the room rises and the temperature difference ΔT (° C) exceeds + T2 (° C), the maximum frequency Fmax (Hz) is controlled at the same F1 (Hz) as the normal control. The cooling capacity is ensured, and the inconvenience that the room does not cool can be prevented. The same applies to heating. If the temperature of the room decreases and the temperature difference ΔT (° C) exceeds + T2 (° C), the maximum frequency Fmax (Hz) is controlled at the same F1 (Hz) as the normal control. Therefore, the heating capacity is ensured, and the inconvenience that the room does not warm can be prevented.

  As described above in detail, when the temperature difference ΔT (° C.) between the set temperature of the indoor units 1 to 4 and the room temperature is less than + T2 (° C.), the maximum frequency Fmax (Hz) of the compressor 101 is set. Between the maximum frequency F0 (Hz) when the temperature difference ΔT (° C.) is 0 and the maximum frequency F1 (Hz) of the compressor 101 when the temperature difference ΔT (° C.) is + T2 (° C.) . Thereby, since the pressure difference between the high pressure and the low pressure in the compressor 101 becomes small, the ratio (COP) of the capacity to the input of the compressor 101 increases, and the operation becomes efficient. Further, when the temperature difference ΔT (° C.) is equal to or greater than + T2 (° C.), the compressor 101 is controlled at the maximum frequency F1 (Hz) during normal operation, so that comfort is maintained. As a result, it is possible to reduce power consumption while ensuring comfort.

Embodiment 2. FIG.
Next, a second embodiment of the present invention will be described.

  In this embodiment, control is performed using a control signal S (%) instead of the maximum frequency Fmax of the compressor.

  FIG. 11 shows the relationship between the maximum frequency (Hz) of the compressor 101 and the control signal S (%). Assuming that the maximum frequency when the total rated capacity of the indoor units that are thermo-on is maximum is F2 (Hz), the control signal S (%) corresponding to F2 is 100 (%), and the frequency F0 (first embodiment) The control signal corresponding to Hz) is S0 (%), and the control signal corresponding to the frequency F1 (Hz) is S1 (%).

  FIG. 12 shows an energy saving mode control process executed when the energy saving mode is selected. As shown in FIG. 12, the controller 201 sets an initial value of the control signal S (%) (step S41). Here, 100 (%) is set as the initial value of the control signal S (%).

  The controller 201 determines whether or not the compressor 101 of the outdoor unit J (J = 51) to be controlled is operating (step S42). If any of the connected indoor units 1 to 4 is thermo-ON, the outdoor unit 51 is in operation, and this determination is affirmed (step S42; Yes).

  Only when the compressor 101 is in operation (thermo-on) (step S42; Yes), the controller 201 executes a temperature difference determination subroutine that detects the room temperature and the set temperature and determines the temperature difference ΔT (° C.). (Step S43). The processing of this subroutine is the same as in the first embodiment.

  Subsequently, the controller 201 executes a control signal determination process subroutine for determining the control signal S (%) based on the temperature difference ΔT (° C.) (step S44). Details of this subroutine will be described later.

  After execution of step S44 or when the compressor 101 is not operating (step S42; No), the controller 201 transmits a control command including the control signal S (%) to the compressor 101 (step S45).

  Subsequently, the controller 201 determines whether or not an energy saving control stop command has been input (step S46). If the energy saving control stop command has not been input (step S46; No), the controller 201 waits for one minute (step S47) and returns to step S42.

  Thus, unless the stop command for energy saving control is input (step S46; No), the controller 201 repeats steps S42 → S43 → S44 → S45 → S46 → S47 at intervals of 1 minute. When the stop command for energy saving control is input (step S46; Yes), the controller 201 returns the control signal S (%) to 100 (%) (step S48), and outputs a control command including the control signal S (%). Then, the data is transmitted to the compressor 101 (step S49), and the process is terminated.

  In this way, the controller 201 obtains the control signal S (%) and transmits the obtained control signal S (%) to the outdoor unit 51. By incorporating control processing into the controller 201 connected to the outdoor unit, the control method according to this embodiment can be applied to an existing outdoor unit, and the application range of the energy saving mode can be expanded.

  In addition, the control processing is incorporated in the outdoor control boxes 117 of the outdoor units 51 to 53, a notification that the energy saving mode is set is sent from the controller 201 to the outdoor unit 51, and the outdoor control box 117 that receives the notification of the energy saving mode is sent. Thus, the control signal S (%) may be obtained and control may be performed. By incorporating the energy saving mode control process in the outdoor control box 117, the controller 201 can be downsized and manufactured at low cost.

  The energy saving mode may be set by the remote controllers 204 to 208. In this case, the fact may be notified directly to the outdoor units 51 to 53 of the system where the remote controller 204 is installed. You may make it notify via. The remote controllers 204 to 208 are provided with an energy saving mode setting function, thereby improving user convenience.

(Control signal decision processing)
Next, a subroutine for the control signal determination process in step S44 in FIG. 12 will be described. FIG. 13 shows a flowchart of a subroutine for determination processing. FIG. 14 shows the relationship between the temperature difference ΔT (° C.) and the control signal S (%) in the master unit.

  As shown in FIG. 14, in the energy saving mode, the control signal S (%) when the temperature difference ΔT (° C.) is 0 (° C.) or less is set to S 0 (%) smaller than S 1 (%). Then, + T2 (° C.) higher than + T1 (° C.) is set, and when the temperature difference ΔT (° C.) becomes + T2 (° C.) or more, the control signal is set to S1 (%). In the range where the temperature difference ΔT (° C.) is larger than 0 (° C.) and lower than + T2 (° C.), the control signal S (%) is proportional to the temperature difference ΔT between S0 (%) and S1 (%). Value. In this subroutine, S0 (%), S1 (%), and + T2 (° C.) are determined.

  As shown in FIG. 13, first, the controller 201 determines a control signal S0 (%) when the temperature difference ΔT (° C.) is 0 (° C.) or less (step S51). The control signal S0 (%) is a control signal corresponding to the frequency F0 (Hz) according to the first embodiment.

  Subsequently, the controller 201 receives the total rated capacity value (total rated capacity) of the indoor units that are thermo-ON from the outdoor unit J (step S52). Subsequently, the controller 201 determines the control signal S1 (%) from the total rated capacity (step S53). The control signal S1 (%) is a control signal corresponding to the frequency F1 (Hz) according to the first embodiment.

  Subsequently, the controller 201 determines the control signal S (%) based on the temperature difference ΔT (° C.) and the control signals S0 (%) and S1 (%) (step S54). Here, when the temperature difference ΔT (° C.) is equal to or greater than + T2 (° C.), the control signal is S1 (%), and the temperature difference ΔT (° C.) of the parent device is between 0 (° C.) and + T 2 (° C.). 14, the control signal S (%) is proportional to the straight line from S0 (%) to S1 (%), and when the temperature difference ΔT (° C.) is 0 (° C.), the control signal S (%) is S0 (%).

  Subsequently, the controller 201 outputs a control signal S (%) to the outdoor unit J as a command. In the case of cooling, the outdoor unit J controls the frequency of the compressor 101 so that the saturation temperature (evaporation temperature) of the refrigerant obtained from the pressure value (low pressure) of the suction pressure sensor 112 matches the target evaporation temperature ET. When the control signal S (%) is received, the frequency is controlled so as not to exceed the maximum frequency corresponding to the control signal S (%). Similarly to the heating, the controller 201 controls the frequency of the compressor 101 so that the condensing temperature of the refrigerant matches the target condensing temperature CT, but when receiving the control signal S (%), the compressor 101 The frequency is controlled so as not to exceed the maximum frequency corresponding to the signal S (%).

  As shown in FIG. 4, the indoor units 1 to 4 repeat thermo-ON and thermo-OFF with ΔT (° C.) as the boundary between −T 1 (° C.) and + T 1 (° C.). Therefore, ΔT (° C.) is usually −T 1 ( ° C) to + T1 (° C). By setting + T2 (° C.) to a value larger than + T1 (° C.), the control signal S (%) is always controlled to a value lower than the value S1 (%) in the normal control, and the differential pressure between the high pressure and the low pressure And the efficiency of the refrigeration cycle is improved. During cooling, if the room temperature rises and ΔT (° C) becomes + T2 (° C) or higher, the control signal S (%) is controlled at the same value S1 as in normal control, so the cooling capacity is secured. The inconvenience that the room does not cool can be prevented. The same applies to heating. If the temperature of the room decreases and the temperature difference ΔT (%) becomes + T2 (° C) or more, the control signal S (%) is controlled at the same value S1 (%) as in normal control. Therefore, the heating capacity is ensured, and the inconvenience that the room does not warm can be prevented.

  As described above in detail, according to this embodiment, the control signal S (%) is used instead of the maximum frequency Fmax (Hz) of the compressor 101. In this way, the frequency reduction rate is constant regardless of the model of the compressor 101, and control becomes easy.

Embodiment 3 FIG.
Next, a third embodiment of the present invention will be described.

  In this embodiment, instead of the maximum frequency Fmax (Hz) of the compressor, a target evaporation temperature ET (° C.) is commanded from the controller 201 to the outdoor unit J from the controller 201 for cooling and a target condensation temperature CT (° C.) for heating.

(Energy-saving control during cooling operation)
FIG. 15 shows the energy saving mode control process provided in the controller 201 for cooling. As shown in FIG. 15, the controller 201 sets an initial value of the target evaporation temperature ET (° C.) (step S61). Here, the same value ET1 (° C.) as that during the operation in the normal mode is set as the initial value.

  The controller 201 determines whether or not the compressor 101 of the outdoor unit J (J = 51) to be controlled is operating (step S62). If any of the connected indoor units 1 to 4 is thermo-ON, the outdoor unit 51 is in operation, and this determination is affirmed (step S62; Yes).

  Only when the compressor 101 is in operation (thermo-on) (step S62; Yes), the controller 201 executes a temperature difference determination processing subroutine that detects the room temperature and the set temperature and determines the temperature difference ΔT (° C.). (Step S63). The processing of this subroutine is the same as in the first and second embodiments.

  Subsequently, the controller 201 executes a subroutine of target evaporation temperature determination processing for determining the target evaporation temperature ET (° C.) based on the temperature difference ΔT (° C.) (step S64). Details of this subroutine will also be described later.

  After step S64 is executed or when the compressor 101 is not operating (step S62; No), the controller 201 transmits a control command including the target evaporation temperature ET to the compressor 101 (step S65).

  Subsequently, the controller 201 determines whether or not an energy saving control stop command has been input (step S66). If the energy-saving control stop command has not been input (step S66; No), the controller 201 waits for one minute (step S67) and returns to step S62.

  Thus, unless the stop command for energy-saving control is input (step S66; No), the controller 201 repeats steps S62 → S63 → S64 → S65 → S66 → S67 at 1 minute intervals. When the energy saving control stop command is input (step S66; Yes), the controller 201 returns the target evaporation temperature ET (° C.) to ET1 (° C.) (step S68), and includes the target evaporation temperature ET (° C.). A command is transmitted to the compressor 101 (step S69), and the process is terminated.

  In this way, the controller 201 obtains the target evaporation temperature ET (° C.) and outputs the obtained target evaporation temperature ET (° C.) to the outdoor unit 51. By incorporating the energy saving mode control processing into the controller 201 connected to the outdoor units 1 to 4, it becomes possible to deal with existing outdoor units and the application range of the energy saving mode can be expanded.

  Further, an energy saving mode control process is incorporated in the outdoor control boxes 117 of the outdoor units 51 to 53, a command for energy saving control is sent from the controller 201 to the outdoor unit 51, and a target is set in the outdoor control box 117 that has received the control command for energy saving control. Control may be performed by obtaining the evaporation temperature ET. By incorporating the energy saving mode control process in the outdoor control box 117, the controller 201 can be downsized and the controller 201 can be manufactured at low cost.

  The energy saving mode may be set by the remote controllers 204 to 208. In this case, the fact may be notified directly to the outdoor units 51 to 53 of the system where the remote controller 204 is installed. You may make it notify via. The remote controllers 204 to 208 are provided with an energy saving mode setting function, thereby improving user convenience.

(Target evaporation temperature determination process)
Next, a subroutine for target evaporation temperature determination processing in step S64 in FIG. 15 will be described. FIG. 16 shows a flowchart of a subroutine for target evaporation temperature determination processing. 17A and 17B show the relationship between the temperature difference ΔT in the master unit and the target evaporation temperature ET (° C.) of the compressor 101.

  As shown in FIG. 17A, in the normal mode, the target evaporation temperature ET (° C.) is constant at ET1 (° C.) regardless of the temperature difference ΔT. In contrast, as shown in FIG. 17B, in the energy saving mode, when the temperature difference ΔT (° C.) is 0 (° C.) or less, the target evaporation temperature ET (° C.) is higher than the temperature ET 1 (° C.) in the normal mode. When the temperature ET0 (° C.) is high and the temperature difference ΔT (° C.) of the master unit is + T2 (° C.) or more, the target evaporation temperature ET (° C.) is ET 1 (° C.) which is the same as in the normal mode. Further, the target evaporation temperature ET (° C.) is determined in proportion to the straight line from ET 0 (° C.) to ET 1 (° C.) when ΔT of the parent machine is 0 (° C.) to T 2 (° C.). Here, ET0 (° C.) is, for example, 9 ° C., and is a temperature at which the relative humidity of the room can be kept at 70% or less.

  As shown in FIG. 16, first, the controller 201 determines a target evaporation temperature ET0 (° C.) when the temperature difference ΔT (° C.) is 0 (° C.) or less (step S71). The target evaporation temperature ET0 (° C.) is set to a temperature ET0 (° C.) lower than the temperature ET1 (° C.) in the normal mode.

  Subsequently, the controller 201 determines a target evaporation temperature ET1 (° C.) when the temperature difference ΔT (° C.) is 0 (° C.) or less (step S72). Here, the target evaporation temperature during operation in the normal mode is set as ET1 (° C.).

  Subsequently, the controller 201 determines a target evaporation temperature ET (° C.) based on the temperature differences ΔT (° C.), E0 (° C.), and E1 (° C.) (step S73). Here, when the temperature difference ΔT (° C.) is equal to or higher than + T2 (° C.), the target evaporation temperature ET (° C.) is ET1 (° C.), and the temperature difference ΔT (° C.) of the parent device is changed from 0 (° C.) to + T2 ( Until the temperature difference ΔT (° C.) is 0 (° C.), as shown in FIG. 17B, the value is proportional to the straight line from ET 0 (° C.) to ET 1 (° C.). The target evaporation temperature ET (° C.) is ET 0 (° C.).

  Subsequently, the controller 201 outputs the control command including the target evaporation temperature ET (° C.) to the outdoor unit J (step S74). In the case of cooling, the outdoor unit J controls the frequency of the compressor 101 so that the refrigerant saturation temperature (evaporation temperature) obtained from the pressure value (low pressure) of the suction pressure sensor 112 matches the target evaporation temperature ET. Since ET0 (° C.) is too high, the amount of dehumidification decreases, so the relative humidity of the room is determined to be 70% or less.

  As shown in FIG. 4, each of the indoor units 1 to 4 has a temperature difference ΔT (° C.) that repeats thermo-on and thermo-off with the temperature of −T1 (° C.) and + T1 (° C.) as a boundary. ) Usually varies between −T1 (° C.) and + T1 (° C.). By setting + T2 (° C) to a value greater than + T1 (° C), the target evaporation temperature ET (° C) is always controlled at a temperature higher than the temperature ET1 (° C) in normal control, improving the efficiency of the refrigeration cycle. To do. If the temperature of the room rises and the temperature difference ΔT (° C) exceeds + T2 (° C), the target evaporation temperature ET (° C) is controlled at the same value ET1 (° C) as when operating in the normal mode. Therefore, the cooling capacity is ensured. Thereby, the inconvenience that the room does not cool can be prevented.

(Energy-saving control during heating operation)
FIG. 18 shows the energy saving mode control process during heating provided in the controller 201. As shown in FIG. 18, the controller 201 sets an initial value of the target condensation temperature CT (° C.) (step S81). Here, the same value CT1 (° C.) as that during the operation in the normal mode is set as the initial value.

  The controller 201 determines whether or not the compressor 101 of the outdoor unit J (J = 51) to be controlled is operating (step S82). If any of the connected indoor units 1 to 4 is thermo-ON, the outdoor unit 51 is in operation, and this determination is affirmed (step S82; Yes).

  Only when the compressor 101 is operating (thermo-on) (step S82; Yes), the controller 201 executes a temperature difference determination subroutine for detecting the room temperature and the set temperature and determining the temperature difference ΔT (° C.) ( Step S83). This subroutine is the same as in the first and second embodiments.

  Subsequently, the controller 201 executes a subroutine of target condensation temperature determination processing for determining the target condensation temperature CT (° C.) based on the temperature difference ΔT (° C.) (step S84). Details of this subroutine will be described later.

  After execution of step S64 or when the compressor 101 is not operating (step S82; No), the controller 201 transmits a control command including the target condensation temperature CT (° C.) to the compressor 101 (step S85).

  Subsequently, the controller 201 determines whether or not an energy saving control stop command has been input (step S86). If the energy saving control stop command is not input (step S86; No), the controller 201 waits for one minute (step S87), and returns to step S82.

  Thus, unless the stop command for energy-saving control is input (step S86; No), the controller 201 repeats steps S82 → S83 → S84 → S85 → S86 → S87 at intervals of 1 minute. When the energy saving control stop command is input (step S86; Yes), the controller 201 returns the target condensing temperature CT (° C.) to CT1 (° C.) (step S88), and includes the target condensing temperature CT (° C.). A command is transmitted to the compressor 101 (step S89), and the process is terminated.

  In this way, the controller 201 obtains the target condensation temperature CT (° C.) and transmits the obtained target condensation temperature CT (° C.) to the outdoor unit 51. By incorporating control processing into the controller 201 connected to the outdoor unit, the control method according to this embodiment can be applied to an existing outdoor unit, and the application range of the energy saving mode can be expanded.

  Further, the energy saving mode control process is incorporated in the outdoor control boxes 117 of the outdoor units 51 to 53, the control command of the energy saving mode is sent from the controller 201 to the outdoor unit 51, and the outdoor control box 117 which has received the control command of the energy saving mode is used. Control may be performed by obtaining the target condensation temperature CT (° C.). By incorporating the energy saving mode control process in the outdoor control box 117, the controller 201 can be downsized and the controller 201 can be manufactured at low cost.

  The energy saving mode may be set by the remote controllers 204 to 208. In this case, the fact may be notified directly to the outdoor units 51 to 53 of the system where the remote controller 204 is installed. You may make it notify via. The remote controllers 204 to 208 are provided with an energy saving mode setting function, thereby improving user convenience.

(Target condensation temperature determination process)
Next, a subroutine for target condensation temperature determination processing in step S84 in FIG. 18 will be described. FIG. 19 shows a flowchart of a subroutine for target condensation temperature determination processing. 20A and 20B show the relationship between the temperature difference ΔT (° C.) and the target condensation temperature CT (° C.) in the parent machine.

  As shown in FIG. 20A, in the normal mode, the target condensation temperature CT (° C.) is constant at CT1 (° C.) regardless of the temperature difference ΔT. On the other hand, as shown in FIG. 20B, in the energy saving mode, when the temperature difference ΔT (° C.) is 0 (° C.) or less, the target condensation temperature CT (° C.) is higher than the temperature CT1 (° C.) in the normal mode. When the temperature is low CT0 (° C.) and the temperature difference ΔT (° C.) of the master unit is + T2 (° C.) or more, the target condensing temperature CT (° C.) is set to CT 1 (° C.) as in the normal mode. In addition, the controller 201 sets the target condensation temperature CT (° C.) in proportion to the straight line from CT 0 (° C.) to CT 1 (° C.) when the temperature difference ΔT (° C.) of the master unit is 0 (° C.) to + T 2 (° C.). To decide.

  As shown in FIG. 19, first, the controller 201 determines a target condensation temperature CT0 (° C.) when the temperature difference ΔT (° C.) is 0 (° C.) or less (step S91). The target condensation temperature CT0 (° C.) is set to a temperature lower than the temperature CT1 (° C.) in the normal mode.

  Subsequently, the controller 201 determines a target condensation temperature CT1 (° C.) when the temperature difference ΔT (° C.) is 0 (° C.) or less (step S92). Here, the target condensing temperature during operation in the normal mode is determined as CT1 (° C.).

  Subsequently, the controller 201 determines a target condensation temperature CT (° C.) based on the temperature difference ΔT (° C.) (step S93). Here, when the temperature difference ΔT (° C.) is equal to or greater than + T2 (° C.), the target condensing temperature CT (° C.) is CT0 (° C.), and the temperature difference ΔT (° C.) of the master unit is changed from 0 (° C.) to + T2 ( 20) until the temperature difference ΔT (° C.) is 0 (° C.), the value is proportional to the straight line from CT 0 (° C.) to CT 1 (° C.). The target condensation temperature CT (° C.) is CT 0 (° C.).

  Subsequently, the controller 201 outputs the target condensation temperature CT to the outdoor unit J as a command. In the case of cooling, the outdoor unit J controls the frequency of the compressor 101 so that the refrigerant saturation temperature (evaporation temperature) obtained from the pressure value (low pressure) of the suction pressure sensor 112 matches the target condensation temperature CT (° C.). To do.

  As shown in FIG. 4, each of the indoor units 1 to 4 has a temperature difference ΔT (° C.) that repeats thermo-on and thermo-off with the temperature of −T1 (° C.) and + T1 (° C.) as a boundary. ) Usually varies between −T1 (° C.) and + T1 (° C.). By setting + T2 (° C) to a value greater than + T1 (° C), the target condensation temperature CT (° C) is always controlled at a temperature lower than the temperature CT1 (° C) in normal control, improving the efficiency of the refrigeration cycle. To do. If the temperature of the room decreases and the temperature difference ΔT (° C.) becomes + T2 (° C.) or more, the target condensation temperature CT (° C.) is controlled at the same value CT1 (° C.) as the normal control. Capability is secured. For this reason, the inconvenience that the room does not warm can be prevented.

  As described above in detail, when the target evaporation temperature ET (° C.) and the target condensation temperature CT (° C.) are directly controlled, the operation of the refrigeration cycle is performed rather than controlling the maximum frequency Fmax of the compressor and the control signal S (%). Since the state is stable, control is facilitated and efficiency is improved.

Embodiment 4 FIG.
Next, a fourth embodiment of the present invention will be described.

  In each of the above embodiments, the intake air temperature T (° C.) of the indoor units 1 to 4 is considered to be room temperature. However, a wireless thermometer is installed in each room to replace the intake air temperature T (° C.) with the wireless temperature. The total temperature T ′ (° C.) may be regarded as room temperature.

  FIG. 21 is a floor plan view of a building to which the air conditioner 100 according to this embodiment is applied. As shown in FIG. 21, the point which the radio | wireless thermo-hygrometer 61 thru | or 71 is installed in the position corresponding to the indoor units 1 thru | or 11 differs from the building which concerns on each said embodiment.

  FIG. 22 shows a side view of the office A. As shown in FIG. 22, a desk 22 and a personal computer 23 are placed in the office room A, and a resident 24 performs office work. The indoor units 1 to 8 are embedded in the ceiling (ceiling built-in type), and are installed behind the ceiling of the office room A. The indoor units 1 to 8 suck air from the back of the ceiling into the indoor unit, and send wind to the office room A through the duct. The wireless temperature / humidity meters 61 to 71 are installed around the occupant 24 such as on the desk 22.

  FIG. 23 shows the configuration of the air conditioning system according to the embodiment of the present invention. As shown in FIG. 23, it differs from the said Embodiment 1 in the point in which the main | base station 202 of the radio | wireless thermohygrometer 61 thru | or 71 is further provided.

  The base unit 202 of the wireless thermohygrometers 61 to 71 is connected to the transmission line 30. The temperature and humidity measured by the wireless thermohygrometers 61 to 71 are received by the master unit 202 and can be transmitted to the controller 201, the outdoor units 51 to 53, and the indoor units 1 to 11 via the transmission line 30.

  In this embodiment, the energy saving mode control process is executed using the temperature T ′ (° C.) of the wireless thermometer instead of the intake air temperature T (° C.) of the indoor unit in the first to third embodiments. By using the temperature T ′ (° C.) of the wireless thermohygrometers 61 to 71 instead of the intake air temperature T (° C.), the ambient temperature of the occupant 24 is accurately detected and control of the energy saving mode is executed. be able to. As a result, the power consumption can be reduced while maintaining the comfort of the occupant 24.

  As described above, according to each of the above-described embodiments, the compressor 101 is operated with the minimum frequency. Therefore, the indoor unit that is the master unit operates continuously, and the other indoor units perform thermo-on and thermo-off. Repeat and adjust the room temperature. Further, when the temperature difference ΔT is + T2 (° C.) or more, the compressor 101 is controlled in the same manner as in the normal operation, so that the cooling capacity and the heating capacity are ensured and the comfort is maintained.

  In the above embodiment, the program to be executed is a computer-readable recording such as a flexible disk, a CD-ROM (Compact Disk Read-Only Memory), a DVD (Digital Versatile Disk), and an MO (Magneto-Optical Disk). A system that executes the above-described processing may be configured by storing and distributing the program on a medium and installing the program.

  Further, the program may be stored in a disk device or the like of a predetermined server device on a communication network such as the Internet, and may be downloaded, for example, superimposed on a carrier wave.

  In addition, when the above functions are realized by sharing an OS (Operating System), or when the functions are realized by cooperation between the OS and an application, only the part other than the OS may be stored in a medium and distributed. You may also download it.

  In addition, this invention is not limited by the said embodiment and drawing. It goes without saying that the embodiments and the drawings can be modified without changing the gist of the present invention.

  The present invention is suitable for a multi-room type air conditioner.

DESCRIPTION OF SYMBOLS 1-11 Indoor unit 22 Desk 23 Personal computer 24 Residents 30 Transmission line 51, 52, 53 Outdoor unit 61-71 Wireless thermohygrometer 100 Air conditioner 101 Compressor 102 Four-way valve 103 Outdoor heat exchanger 104 Liquid side main pipe 105 Liquid side branch pipe 106 Expansion valve 107 Indoor heat exchanger 108 Gas side branch pipe 109 Gas side main pipe 110 Accumulator 111 Discharge pressure sensor 112 Suction pressure sensor 113 Outside air temperature sensor 114 Liquid pipe temperature sensor 115 Gas pipe temperature sensor 116 Intake air temperature Sensor 117 Outdoor control box 118 Indoor control box 201 Controller 202 Master unit 203 Power feeder 204, 205, 206, 207, 208 Remote controller A, D Office B, C Meeting room

Claims (8)

  1. A control device that controls an air conditioner including an outdoor unit connected via a refrigerant circuit, and a plurality of indoor units that switch between thermo-on and thermo-off based on a temperature difference between a set temperature and a room temperature ,
    Among the plurality of the indoor unit, the indoor unit in which the temperature difference is maximum, is set as the master unit is a heat load up to the indoor unit,
    The indoor unit that newly has the maximum temperature difference is set as a candidate for the master unit,
    When setting the master unit for the first time, or when the indoor unit already set as the master unit is thermo-off, or when the temperature difference in the candidate for the master unit becomes a predetermined value or more, Set a candidate for the parent machine as the new parent machine,
    Command generation means for generating a command to the compressor of the outdoor unit according to the temperature difference in the base unit,
    Control device.
  2. A controller that can communicate with the outdoor unit and the indoor unit.
    The control device according to claim 1.
  3. Built into the outdoor unit,
    Operates when energy saving mode is set from the host device.
    The control device according to claim 1.
  4. Further comprising a remote controller for operating and stopping the indoor unit,
    Operates when the energy saving mode is set by the remote controller,
    The control apparatus according to claim 1, wherein the control apparatus is a control apparatus.
  5. The intake air temperature of the indoor unit is the indoor temperature.
    The control device according to any one of claims 1 to 4, wherein
  6. The temperature measured by a wireless thermometer installed corresponding to each indoor unit is the indoor temperature,
    The control device according to any one of claims 1 to 5, wherein
  7. A control method for controlling an air conditioner comprising an outdoor unit connected via a refrigerant circuit, and a plurality of indoor units in which thermo-on and thermo-off are switched based on a temperature difference between a set temperature and a room temperature ,
    Among the plurality of the indoor unit, the indoor unit in which the temperature difference is maximum, is set as the master unit is a heat load up to the indoor unit,
    The indoor unit that newly has the maximum temperature difference is set as a candidate for the master unit,
    When setting the master unit for the first time, or when the indoor unit already set as the master unit is thermo-off, or when the temperature difference in the candidate for the master unit becomes a predetermined value or more, Set a candidate for the parent machine as the new parent machine,
    Generate a command to the compressor of the outdoor unit according to the temperature difference in the base unit,
    Control method.
  8. A computer that controls an air conditioner including an outdoor unit connected via a refrigerant circuit, and a plurality of indoor units that switch between thermo-on and thermo-off based on a temperature difference between a set temperature and a room temperature ,
    Among the plurality of the indoor unit, the indoor unit in which the temperature difference is maximum, is set as the master unit is a heat load up to the indoor unit,
    The indoor unit that newly has the maximum temperature difference is set as a candidate for the master unit,
    When setting the master unit for the first time, or when the indoor unit already set as the master unit is thermo-off, or when the temperature difference in the candidate for the master unit becomes a predetermined value or more, Set a candidate for the parent machine as the new parent machine,
    Command generating means for generating a command to the compressor of the outdoor unit according to the temperature difference in the master unit,
    Program to function as.
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