JP5900472B2 - Refrigeration apparatus and control method of refrigeration apparatus - Google Patents

Description

  The present invention relates to a refrigeration apparatus and a control method thereof, and more particularly to a refrigeration apparatus that performs a vapor compression refrigeration cycle by circulating a refrigerant and a control method thereof.

  A refrigerating apparatus such as an air conditioner has a compressor that compresses a refrigerant, a heat source side heat exchanger and a use side heat exchanger that perform heat exchange with the refrigerant, and a decompression mechanism that depressurizes the refrigerant. Is provided with a refrigerant circuit that performs a vapor compression refrigeration cycle by circulating the refrigerant. In such a refrigeration apparatus, when the control parameter for controlling the refrigerant circuit greatly fluctuates due to a disturbance or the like, the control parameter greatly deviates from the control target value, so that the suction side of the compressor enters a gas-liquid two-phase state. There is a high possibility that some trouble such as the refrigeration apparatus will be overheated. In order to escape from problems caused by such large fluctuations in control parameters, the control parameters are converged to the control target value as soon as possible.

  For example, in the cooling device and the control method thereof disclosed in Patent Document 1 (Japanese Patent Laid-Open No. 5-10603), the opening degree of the expansion valve (compression mechanism) is adjusted by applying fuzzy inference to PID (proportional integral derivative) control. Technology is shown. By using fuzzy reasoning, it is possible to construct not only control during normal operation but also control that can appropriately cope with a case where the control parameter fluctuates greatly due to disturbance or the like.

  However, if a fuzzy inference rule or the like is applied to PID (proportional integral derivative) control, various conditions must be determined in detail by experiments on the actual cooling device. Therefore, it is very troublesome to implement fuzzy reasoning on the actual cooling device. Moreover, even if fuzzy inference is implemented with a lot of effort, the output value will be the same if the input value is the same in fuzzy inference. Therefore, it is difficult to control the transient state and the normal state separately in an excessive change. Cases also arise.

  The problem of the present invention is that the refrigerant circuit can be quickly returned to the normal state when the control parameter fluctuates excessively from the control target value, and stable control is maintained in the normal state of the refrigerant circuit. It is to provide a refrigeration apparatus.

A refrigeration apparatus according to a first aspect of the present invention includes an actuator, a refrigerant circuit that adjusts a state change of the refrigerant in a vapor compression refrigeration cycle performed by circulating the refrigerant by the actuator, the refrigerant circuit, A sensor that detects the state quantity of the refrigerant related to the change in the state of the refrigerant in the cycle and outputs the current state quantity, and the operation amount of the actuator deviates so that the control parameter calculated from the current state quantity approaches the control target value and a control unit for changing a proportional integral control or proportional-integral-derivative control with an integral term proportional to the integral of the difference between the proportional term proportional to the control device, first the operation of the behavior changes amount than the proportional gain of the operation amount changing operation as the first operation amount change operation proportional gain is configured capable of switching a large second operation amount change operation, the control eye Using the first operation amount change operation when an excessive variation in which the deviation exceeds the threshold value and the control parameter is not detected, in the excessive fluctuations when the control parameter is approaching the control target value The first operation amount changing operation is switched to the second operation amount changing operation.

  In the refrigeration apparatus according to the first aspect, an excessive variation in which the control parameter greatly fluctuates due to disturbance or the like is detected based on whether or not the control parameter deviates from the control target value by a predetermined value or more. In such an excessive fluctuation, the control device changes the operation amount of the actuator by using the second operation amount changing operation to quickly bring the control parameter close to the control target value, and from the inappropriate state of the refrigerant circuit at the time of the excessive fluctuation. Make sure you can escape quickly. On the other hand, the control device changes the operation amount of the actuator using the first operation amount changing operation without using the second operation amount changing operation except in the case of excessive fluctuation, thereby preventing normal hunting.

Further, since it is only determined whether or not the deviation between the control target value and the control parameter exceeds the threshold value, it is easy to determine the excessive fluctuation.

Further, when the control parameter is approaching the control target value, the control parameter can be quickly brought closer to the control target value by switching to the second operation amount changing operation. It is easily known from the relationship between target values.

The refrigeration apparatus according to the second aspect of the present invention is the refrigeration apparatus according to the first aspect , in which the control device determines that an excessive fluctuation has occurred and the control parameter is approaching the control target value. When the control parameter changes in a direction away from the control target value after switching from the operation to the second operation amount changing operation, the second operation amount changing operation is returned to the first operation amount changing operation.

In refrigeration apparatus of the second view point, when the control parameter is a change in the direction away from the control target value when the control parameter is determined that excessive variation occurs is close to the control target value, the second operation amount By returning from the change operation to the first operation amount change operation, the operation that prevents the control parameter from reaching the control target value is reduced, control instability is suppressed, and the control parameter converges to the control target value. Can be expedited.

The refrigeration apparatus according to the third aspect of the present invention is the refrigeration apparatus according to the first aspect or the second aspect . After the control device switches to the second operation amount changing operation, the control parameter exceeds the control target value and then When the control target value is reached, it is determined that the excessive fluctuation has ended, and when it is determined that the excessive fluctuation has ended, the second operation amount changing operation is switched to the first operation amount changing operation.

In the refrigeration apparatus according to the third aspect, instead of switching from the second operation amount changing operation to the first operation amount changing operation immediately after the control parameter reaches the control target value, the control parameter becomes the control target value for the second time. Since the second operation amount changing operation is switched to the first operation amount changing operation at the time point, it is possible to extend the period until the control parameter converges to the control target value by the second operation amount changing operation.

The refrigeration apparatus according to the fourth aspect of the present invention forcibly determines the second operation amount based on an elapsed time after switching to the second operation amount changing operation after switching to the second operation amount changing operation. The change operation is switched to the first operation amount change operation.

  A refrigeration apparatus according to a sixth aspect of the present invention is the refrigeration apparatus according to any one of the third to fifth aspects, wherein the control device is an integral proportional to a deviation term and an integral of the deviation. The operation change unit is set so that the proportional gain of the second operation amount changing operation is larger than the proportional gain of the first operation amount changing operation.

  In the refrigeration apparatus of the sixth aspect, it is only necessary to change the proportional gain of the proportional integral control by the first operation amount changing operation and the second operation amount changing operation.

  In the refrigeration apparatus according to the seventh aspect of the present invention, in the refrigeration apparatus according to any one of the first to sixth aspects, the refrigerant circuit heat-source-side heat that exchanges heat between the compressor that compresses the refrigerant and the refrigerant. An exchanger and a use-side heat exchanger, a heat-source-side fan that blows air to the heat-source-side heat exchanger, a use-side fan that blows air to the use-side heat exchanger, and a decompression mechanism that can adjust the decompression of the refrigerant by the valve opening degree. And the actuator includes at least one of a compressor, a heat source side fan, a use side fan, and a pressure reducing mechanism.

  In the refrigeration apparatus according to the seventh aspect, at the time of excessive fluctuation, the control device changes the operation amount of at least one of the compressor, the heat source side fan, the use side fan, and the pressure reducing mechanism using the second operation amount changing operation. As a result, the control parameter is brought close to the control target value quickly so that the refrigerant circuit can quickly escape from the inappropriate state of the refrigerant circuit at the time of excessive fluctuation. On the other hand, the control device operates at least one of the compressor, the heat source side fan, the use side fan, and the pressure reducing mechanism by using the first operation amount changing operation without using the second operation amount changing operation except during excessive fluctuation. By changing the amount, normal hunting is prevented.

  A control method for a refrigeration apparatus according to an eighth aspect of the present invention includes an actuator, a refrigerant circuit that adjusts the state change of the refrigerant in a vapor compression refrigeration cycle performed by circulating the refrigerant, and the refrigerant circuit. And a sensor that detects a state quantity of the refrigerant related to a change in the state of the refrigerant in the refrigeration cycle and outputs a current state quantity, and an actuator so that a control parameter calculated from the current state quantity approaches a control target value The control method of the refrigeration apparatus for changing the operation amount of the refrigeration apparatus, wherein a change detection step for detecting an excessive change such that the control parameter deviates from a control target value by a predetermined value or more and a first operation in which the operation amount change operation is different from each other An operation change step capable of switching between the amount change operation and the second operation amount change operation. In the operation change step, an excessive variation is detected. If not, the first operation amount changing operation is used, and when an excessive fluctuation is detected, the control parameter is switched to the second operation amount changing operation that can be brought closer to the control target value faster than the first operation amount changing operation. It is.

  In the refrigeration apparatus according to the eighth aspect, the fluctuation detection step unit detects an excessive fluctuation in which the control parameter greatly fluctuates due to disturbance or the like depending on whether or not the control parameter deviates from the control target value by a predetermined value or more. When such an excessive change occurs, the operation change step uses the second operation amount change operation to change the actuator operation amount to quickly bring the control parameter close to the control target value. Get ready to escape quickly from On the other hand, in the operation change step, normal operation hunting is prevented by changing the operation amount of the actuator using the first operation amount changing operation without using the second operation amount changing operation except in the case of excessive fluctuation.

  In the control method of the refrigeration apparatus according to the first aspect of the present invention or the refrigeration apparatus according to the eighth aspect, when the control parameter fluctuates excessively from the control target value, the second operation amount changing operation is used to change the refrigerant. The circuit can be quickly returned to the normal state, and stable control is maintained using the first operation amount changing operation in the normal state of the refrigerant circuit.

  In the refrigeration apparatus according to the second aspect of the present invention, the determination of the excessive fluctuation is simplified, and the control in the control apparatus is simplified.

  In the refrigeration apparatus according to the third aspect of the present invention, control parameter fluctuations can be suppressed, and control for switching from the first operation amount changing operation to the second operation amount changing operation is simplified.

  In the refrigeration apparatus according to the fourth aspect of the present invention, it is determined that an excessive fluctuation has occurred, and the control parameter is more stable when the control parameter changes in a direction away from the control target value when the control parameter approaches the control target value. Control can be maintained.

  In the refrigeration apparatus according to the fifth aspect of the present invention, the period until the control parameter converges to the control target value by the second operation amount changing operation can be increased, and the fluctuation of the control parameter can be suppressed.

  In the refrigeration apparatus according to the sixth aspect of the present invention, the control is simplified because only the proportional gain of the proportional integral control is changed by the first operation amount changing operation and the second operation amount changing operation.

  In the refrigeration apparatus according to the seventh aspect of the present invention, when the control parameter fluctuates excessively from the control target value, the refrigerant circuit can be quickly returned to the normal state using the second operation amount changing operation. In addition, in the normal state of the refrigerant circuit, stable control is maintained using the first operation amount changing operation.

The circuit diagram which shows the outline | summary of a structure of the air conditioning apparatus which concerns on this invention. The block diagram for demonstrating the control system of the air conditioning apparatus of FIG. The flowchart for demonstrating the example of control at the time of the cooling of the indoor expansion valve of an indoor side control apparatus. The graph for demonstrating the example of the conventional control at the time of the cooling of the indoor expansion valve of an indoor side control apparatus. The graph for demonstrating the example of control at the time of the cooling of the indoor expansion valve of an indoor side control apparatus. The flowchart for demonstrating the example of control at the time of the heating of the indoor expansion valve of an indoor side control apparatus. The flowchart for demonstrating the example of control at the time of cooling of the compressor of an outdoor side control apparatus. The graph for demonstrating the example of control at the time of air_conditioning | cooling of the compressor of an outdoor side control apparatus. The flowchart for demonstrating the example of control at the time of the cooling of the indoor expansion valve of the indoor side control apparatus which concerns on a modification. The graph for demonstrating the control example at the time of the cooling of the indoor expansion valve of the indoor side control apparatus which concerns on a modification. The flowchart for demonstrating the example of control at the time of the heating of the indoor expansion valve of the indoor side control apparatus which concerns on a modification. The flowchart for demonstrating the example of control at the time of the cooling of the compressor of the outdoor side control apparatus which concerns on a modification. The graph for demonstrating the example of control at the time of the cooling of the compressor of the outdoor side control apparatus which concerns on a modification.

(1) Configuration of Air Conditioner In the following description, an example of an air conditioner used for air conditioning in a room such as a building by performing a vapor compression refrigeration cycle operation as a refrigeration apparatus according to an embodiment. Cite. FIG. 1 is a circuit diagram showing an outline of a configuration of an air conditioner that is a refrigeration apparatus according to an embodiment of the present invention. An air conditioner 10 shown in FIG. 1 is mainly composed of an outdoor unit 20 as one heat source unit and a plurality of (three in the present embodiment) usage units connected in parallel thereto. And a liquid refrigerant communication pipe 71 and a gas refrigerant communication pipe 72 as refrigerant communication pipes connecting the outdoor unit 20 and the indoor units 40, 50, 60 to each other. That is, in the vapor compression refrigerant circuit 11 of the air conditioning apparatus 10 of the present embodiment, the outdoor unit 20, the indoor units 40, 50, and 60, the liquid refrigerant communication pipe 71, and the gas refrigerant communication pipe 72 are connected. Is made up of.

(1-1) Indoor unit The indoor units 40, 50, and 60 are installed in one room 1 such as a conference room, for example, by embedding or hanging in a ceiling of a room such as a building or by hanging on a wall surface of the room. Has been. Since the indoor units 40 and the indoor units 50 and 60 have the same configuration, only the configuration of the indoor unit 40 will be described here, and the configurations of the indoor units 50 and 60 are shown for each part of the indoor unit 40, respectively. The reference numbers 50 and 60 are used instead of the reference numbers 40 and description of each part is omitted.

  The indoor unit 40 mainly has an indoor refrigerant circuit 11a (a indoor refrigerant circuit 11b in the indoor unit 50 and an indoor refrigerant circuit 11c in the indoor unit 60) constituting a part of the refrigerant circuit 11. This indoor side refrigerant circuit 11a mainly has an indoor expansion valve 41 as an expansion mechanism and an indoor heat exchanger 42 as a use side heat exchanger. In the present embodiment, the indoor expansion valves 41, 51, 61 are provided in the indoor units 40, 50, 60, respectively, as the expansion mechanism. However, the present invention is not limited to this, and the expansion mechanism (including the expansion valve) is an outdoor unit. 20 may be provided, or may be provided in 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 the flow rate of the refrigerant flowing in the indoor refrigerant circuit 11a, and blocks passage of the refrigerant. Is also possible.

  The indoor heat exchanger 42 is, for example, a cross fin type fin-and-tube heat exchanger configured by heat transfer tubes and a large number of fins. The indoor heat exchanger 42 is a heat exchanger that functions as a refrigerant evaporator during cooling operation to cool indoor air and functions as a refrigerant condenser during heating operation to heat indoor air.

  The indoor unit 40 sucks indoor air into the unit, exchanges heat with the refrigerant in the indoor heat exchanger 42, and then supplies the indoor air after heat exchange into the room as supply air. 43. The indoor fan 43 is a fan capable of changing the air volume supplied to the indoor heat exchanger 42 within a predetermined air volume range. For example, a centrifugal fan or a multiblade fan driven by a motor 43m formed of a DC fan motor or the like. Etc. In this indoor fan 43, a fixed air volume mode that sets three types of fixed air volumes, a weak wind with the smallest air volume, a strong wind with the largest air volume, and a medium wind between the weak wind and the strong wind, and the superheat degree SH and the supercooling. It is possible to select and set either an air volume automatic mode that automatically changes between low and high winds depending on the degree SC, or an air volume setting mode that is manually changed by an input device such as a remote controller. . That is, if the user selects one of “weak wind”, “medium wind”, and “strong wind” using a remote controller, for example, the air volume is fixed in the weak wind mode and “automatic” is selected. In this case, the air volume automatic mode in which the air volume is automatically changed according to the operation state is set. Here, a configuration in which the fan tap of the air volume of the indoor fan 43 is switched in three stages of “weak wind”, “medium wind”, and “strong wind” is described. The indoor fan air volume Ga, which is the air volume of the indoor fan 43, can be derived from, for example, calculation using the rotation speed of the motor 43m as a parameter. In addition, there are a method of deriving the indoor fan air volume Ga from a calculation based on the current value of the motor 43m, a method of deriving from a calculation based on a set fan tap, and the like.

  The indoor unit 40 is provided with various sensors. On the liquid side of the indoor heat exchanger 42, the refrigerant temperature (that is, the saturation temperature equivalent to the condensation pressure during heating operation (hereinafter referred to as the condensation temperature) Tc or the saturation temperature corresponding to the evaporation pressure during cooling operation (hereinafter referred to as the evaporation temperature). ) A liquid side temperature sensor 44 for detecting a refrigerant temperature corresponding to Te) is provided. A gas side temperature sensor 45 that detects the temperature of the refrigerant is provided on the gas side of the indoor heat exchanger 42. An indoor temperature sensor 46 that detects the temperature of indoor air flowing into the unit (that is, the indoor temperature Tr) is provided on the indoor air intake side of the indoor unit 40. As the liquid side temperature sensor 44, the gas side temperature sensor 45, and the room temperature sensor 46, for example, a thermistor can be used. The indoor unit 40 also includes an indoor side control device 47 that controls the operation of each part constituting the indoor unit 40. The indoor-side control device 47 includes an air-conditioning capacity calculation unit 47a that calculates the current air-conditioning capacity and the like in the indoor unit 40, and a required evaporation temperature Ter or a required condensing temperature required to exhibit the capacity based on the current air-conditioning capacity. And a required temperature calculation unit 47b for calculating Tcr (see FIG. 2). The indoor control device 47 includes a microcomputer, a memory 47c, and the like provided for controlling the indoor unit 40, and a remote controller (not shown) for individually operating the indoor unit 40. It is possible to exchange control signals and the like with each other, and exchange control signals and the like with the outdoor unit 20 via the transmission line 80a.

(1-2) Outdoor unit The outdoor unit 20 is installed outside a building or the like, and is connected to the indoor units 40, 50, and 60 via a liquid refrigerant communication pipe 71 and a gas refrigerant communication pipe 72. The refrigerant circuit 11 is configured together with the machines 40, 50 and 60. The outdoor unit 20 mainly has an outdoor refrigerant circuit 11 d that constitutes a part of the refrigerant circuit 11. This outdoor refrigerant circuit 11d mainly includes 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 closing valve 26 and a gas side closing valve 27 are provided.

  The compressor 21 is a compressor whose operating capacity can be varied, and is a positive displacement compressor driven by a motor 21m whose rotation speed is controlled by an inverter. In addition, although the outdoor unit 20 shown here has one compressor 21, the number of compressors may be two or more when the number of indoor units connected is large.

  The four-way switching valve 22 is a valve for switching the direction of refrigerant flow. During the cooling operation, the outdoor heat exchanger 23 functions as a refrigerant condenser compressed by the compressor 21, and the indoor heat exchangers 42, 52, 62 serve as refrigerant evaporators condensed in the outdoor heat exchanger 23. In order to function, the discharge side of the compressor 21 and the gas side of the outdoor heat exchanger 23 are connected, and the suction side (specifically, the accumulator 24) of the compressor 21 and the gas refrigerant communication pipe 72 side are connected. Connected (cooling operation state: refer to the solid line of the four-way switching valve 22 in FIG. 1). On the other hand, during the heating operation, the indoor heat exchangers 42, 52, 62 function as the refrigerant condenser compressed by the compressor 21, and the refrigerant evaporator condensed in the indoor heat exchangers 42, 52, 62. In order to make the outdoor heat exchanger 23 function, the discharge side of the compressor 21 and the gas refrigerant communication pipe 72 side are connected, and the suction side of the compressor 21 and the gas side of the outdoor heat exchanger 23 are connected. (Heating operation state: see broken line of four-way switching valve 22 in FIG. 1).

  The outdoor heat exchanger 23 is, for example, a cross fin type fin-and-tube heat exchanger, and is a device for exchanging heat between air and a refrigerant in order to use air as a heat source. The outdoor heat exchanger 23 is a heat exchanger that functions as a refrigerant condenser during the cooling operation and functions as a refrigerant evaporator during the heating operation. The outdoor heat exchanger 23 has a gas side connected to the four-way switching valve 22 and a liquid side connected to the outdoor expansion valve 38.

  The outdoor expansion valve 38 is downstream of the outdoor heat exchanger 23 in the refrigerant flow direction in the refrigerant circuit 11 when performing a cooling operation in order to adjust the pressure, flow rate, and the like of the refrigerant flowing in the outdoor refrigerant circuit 11d. It is an electric expansion valve arrange | positioned in. That is, 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 a blower for sucking outdoor air into the unit, exchanging heat with the refrigerant in the outdoor heat exchanger 23, and then discharging it to the outside. The outdoor fan 28 is a fan capable of changing the air volume of air supplied to the outdoor heat exchanger 23, and is, for example, a propeller fan driven by a motor 28m composed of a DC fan motor or the like.

  The liquid side closing valve 26 and the gas side closing valve 27 are valves provided at connection ports with the liquid refrigerant communication pipe 71 and the gas refrigerant communication pipe 72. The liquid side shut-off valve 26 is disposed downstream of the outdoor expansion valve 38 and upstream of the liquid refrigerant communication pipe 71 in the refrigerant flow direction in the refrigerant circuit 11 when performing the cooling operation, and prevents passage of the refrigerant. It is possible to block. The gas side closing valve 27 is connected to the four-way switching valve 22 and can block the passage of the refrigerant.

  Further, the outdoor unit 20 includes a suction pressure sensor 29 that detects a suction pressure of the compressor 21 (that is, a refrigerant pressure corresponding to the evaporation pressure Pe during the cooling operation), and a discharge pressure of the compressor 21 (that is, a heating operation). A discharge pressure sensor 30 that detects a refrigerant pressure corresponding to the condensation pressure Pc at the time), a suction temperature sensor 31 that detects a suction temperature of the compressor 21, and a discharge temperature sensor 32 that detects a discharge temperature of the compressor 21. Is provided. An outdoor temperature sensor 36 for detecting the temperature of the outdoor air flowing into the unit (that is, the outdoor temperature) is provided on the outdoor air suction port side of the outdoor unit 20. As the suction temperature sensor 31, the discharge temperature sensor 32, and the outdoor temperature sensor 36, for example, a thermistor can be used. In addition, the outdoor unit 20 includes an outdoor control device 37 that controls the operation of each unit constituting the outdoor unit 20. As shown in FIG. 2, the outdoor side control device 37 determines a target evaporation temperature Tet or a target condensation temperature Tct (or a target evaporation temperature difference ΔTet or a target condensation temperature difference ΔTct) for controlling the operation capacity of the compressor 21. A target value determination unit 37a. The outdoor control device 37 includes a microcomputer (not shown) provided to control the outdoor unit 20, an inverter circuit that controls the memory 37b, the motor 21m, and the like. Control signals and the like can be exchanged between the 50 and 60 indoor control devices 47, 57 and 67 via the transmission line 80a. That is, the indoor control devices 47, 57, and 67, the outdoor control device 37, and the transmission line 80a that connects them constitute an operation control device 80 that performs operation control of the entire air conditioner 10. .

  As shown in FIG. 2, the operation control device 80 includes a suction pressure sensor 29, a discharge pressure sensor 30, a suction temperature sensor 31, a discharge temperature sensor 32, an outdoor temperature sensor 36, liquid side temperature sensors 44, 54 and 64, gas, The side temperature sensors 45, 55, 65 and the indoor temperature sensors 46, 56, 66 are connected so as to receive detection signals. In addition, the operation control device 80 can control the outdoor unit 20 and the indoor units 40, 50, 60 based on these detection signals and the like, the compressor 21, the four-way switching valve 22, the outdoor fan 28, the outdoor unit. The expansion valve 38, the indoor expansion valve, 41, 51, 61 and the indoor fans 43, 53, 63 are connected. Furthermore, various data for controlling the air conditioner 10 are stored in the memories 37b, 47c, 57c, and 67c constituting the operation control device 80.

(1-3) Refrigerant communication pipe The liquid refrigerant communication pipe 71 and the gas refrigerant communication pipe 72 are refrigerant pipes constructed on site when the air conditioner 10 is installed at an installation location such as a building. And what has various lengths and pipe diameters is used according to installation conditions, such as a combination of an outdoor unit and an indoor unit. For example, when the air conditioner 10 is newly installed in a building or the like, it is appropriate for the air conditioner 10 according to the installation conditions such as the length and pipe diameter of the liquid refrigerant communication pipe 71 and the gas refrigerant communication pipe 72. A sufficient amount of refrigerant is filled.

  As described above, the indoor refrigerant circuits 11a, 11b, and 11c, the outdoor refrigerant circuit 11d, the liquid refrigerant communication pipe 71, and the gas refrigerant communication pipe 72 are connected, and the refrigerant circuit 11 of the air conditioner 10 is configured. Has been. The air conditioner 10 is operated by switching the cooling operation and the heating operation by the four-way switching valve 22 by the operation control device 80 including the indoor side control devices 47, 57, 67 and the outdoor side control device 37. In addition, the control of each device of the outdoor unit 20 and the indoor units 40, 50, 60 is performed according to the operation load of each indoor unit 40, 50, 60.

(2) Operation of Air Conditioner (2-1) Cooling Operation First, the cooling operation will be described with reference to FIG. During the cooling operation, the four-way switching valve 22 is in the state shown by the solid line in FIG. 1, that is, the discharge side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23 and the suction side of the compressor 21 is the gas side. It is in a state where it is connected to the gas side of the indoor heat exchangers 42, 52, 62 via the closing valve 27 and the gas refrigerant communication pipe 72. Here, the outdoor expansion valve 38 is fully opened. The liquid side closing valve 26 and the gas side closing valve 27 are in an open state. The indoor expansion valve 41 is adjusted in opening degree so that the superheat degree SH1 of the refrigerant at the outlet of the indoor heat exchanger 42 (that is, the gas side of the indoor heat exchanger 42) becomes the target superheat degree SHt1, and the indoor expansion valve 51 The opening degree is adjusted so that the superheat degree SH2 of the refrigerant at the outlet of the indoor heat exchanger 52 (that is, the gas side of the indoor heat exchanger 52) becomes the target superheat degree SHt2, and the indoor expansion valve 61 is The opening degree of the refrigerant is adjusted so that the superheat degree SH3 of the refrigerant at the outlet 62 (that is, the gas side of the indoor heat exchanger 62) becomes the target superheat degree SHt3.

  The target superheat degrees SHt1, SHt2, and SHt3 are set to optimum temperature values so that the indoor temperatures Tr1, Tr2, and Tr3 converge to the set temperatures Ts1, Ts2, and Ts3 within a predetermined superheat degree range. The superheat degree SH1, SH2, SH3 of the refrigerant at the outlets of the indoor heat exchangers 42, 52, 62 is determined based on the refrigerant temperature values (Tg) detected by the gas side temperature sensors 45, 55, 65. It is detected by subtracting the refrigerant temperature value (corresponding to the evaporation temperature Te) detected by 44, 54, and 64, respectively. However, the superheat levels SH1, SH2, and SH3 of the refrigerant at the outlets of the indoor heat exchangers 42, 52, and 62 are not limited to being detected by the above-described method, but may be detected by the suction pressure sensor 29. The suction pressure may be converted into a saturation temperature value corresponding to the evaporation temperature Te and detected by subtracting the saturation temperature value of the refrigerant from the refrigerant temperature values detected by the gas side temperature sensors 45, 55, 65.

  Although not adopted in the present embodiment, a temperature sensor that detects the temperature of the refrigerant flowing in each of the indoor heat exchangers 42, 52, and 62 is provided and corresponds to the evaporation temperature Te detected by this temperature sensor. By subtracting the refrigerant temperature value from the refrigerant temperature value detected by the gas side temperature sensors 45, 55, and 65, the superheat degrees SH1, SH2, and SH3 of the refrigerant at the outlets of the indoor heat exchangers 42, 52, and 62, respectively. You may make it detect.

  When the compressor 21, the outdoor fan 28, and the indoor fans 43, 53, 63 are operated in the state of the refrigerant circuit 11, the low-pressure gas refrigerant is sucked into the compressor 21 and compressed to become a high-pressure gas refrigerant. Thereafter, the high-pressure gas refrigerant is sent to the outdoor heat exchanger 23 via the four-way switching valve 22, exchanges heat with the outdoor air supplied by the outdoor fan 28, and condenses to form a high-pressure liquid refrigerant. Become. Then, the high-pressure liquid refrigerant is sent to the indoor units 40, 50, 60 via the liquid side closing valve 26 and the liquid refrigerant communication pipe 71.

  The high-pressure liquid refrigerant sent to the indoor units 40, 50, 60 is decompressed to near the suction pressure of the compressor 21 by the indoor expansion valves 41, 51, 61, respectively, and becomes low-pressure gas-liquid two-phase refrigerant. Are sent to the indoor heat exchangers 42, 52, and 62, exchange heat with indoor air in the indoor heat exchangers 42, 52, and 62, respectively, and evaporate into low-pressure gas refrigerant.

  The low-pressure gas refrigerant is sent to the outdoor unit 20 via the gas refrigerant communication pipe 72 and flows into the accumulator 24 via the gas-side closing valve 27 and the four-way switching valve 22. Then, the low-pressure gas refrigerant that has flowed into the accumulator 24 is again sucked into the compressor 21. As described above, in the air conditioner 10, the outdoor heat exchanger 23 is condensed as a refrigerant condenser compressed in the compressor 21, and the indoor heat exchangers 42, 52, and 62 are condensed in the outdoor heat exchanger 23. It is possible to perform a cooling operation that functions as an evaporator for the refrigerant that is sent later through the liquid refrigerant communication pipe 71 and the indoor expansion valves 41, 51, 61. In the air conditioner 10, the indoor units 40, 50, 60 do not have a mechanism for adjusting the pressure of the refrigerant on the gas side of the indoor heat exchangers 42, 52, 62. , 52 and 62 are common pressures.

(2-2) Heating Operation Next, the heating operation will be described with reference to FIG. During the heating operation, the four-way switching valve 22 is in the state indicated by the broken line in FIG. 1 (heating operation state), that is, the discharge side of the compressor 21 is exchanged indoors via the gas side closing valve 27 and the gas refrigerant communication pipe 72. The compressor 42, 52, 62 is connected to the gas side, and the suction side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23. The opening of the outdoor expansion valve 38 is adjusted in order to reduce the refrigerant flowing into the outdoor heat exchanger 23 to a pressure at which the refrigerant can be evaporated in the outdoor heat exchanger 23 (that is, the evaporation pressure Pe). Yes. Moreover, the liquid side closing valve 26 and the gas side closing valve 27 are opened. The indoor expansion valves 41, 51, 61 are adjusted in opening degree so that the refrigerant subcooling degrees SC1, SC2, SC3 at the outlets of the indoor heat exchangers 42, 52, 62 become the target subcooling degrees SCt1, SCt2, SCt3, respectively. It has come to be. The target supercooling degrees SCt1, SCt2, and SCt3 are set so that the indoor temperatures Tr1, Tr2, and Tr3 converge to the set temperatures Ts1, Ts2, and Ts3 within the supercooling degree range that is specified according to the operation state at that time. The optimum temperature value is set. The subcooling degree SC1, SC2, SC3 of the refrigerant at the outlets of the indoor heat exchangers 42, 52, 62 sets 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. This is detected by subtracting the refrigerant temperature value detected by the liquid side temperature sensors 44, 54, and 64 from the saturation temperature value of the refrigerant.

  Although not adopted in the present embodiment, a temperature sensor that detects the temperature of the refrigerant flowing in each of the indoor heat exchangers 42, 52, and 62 is provided, and the refrigerant corresponding to the condensation temperature Tc detected by this temperature sensor. By subtracting the temperature value from the refrigerant temperature value detected by the liquid side temperature sensors 44, 54, 64, the subcooling degrees SC1, SC2, SC3 of the refrigerant at the outlets of the indoor heat exchangers 42, 52, 62 are detected. You may do it.

  When the compressor 21, the outdoor fan 28, and the indoor fans 43, 53, 63 are operated in the state of the refrigerant circuit 11, the low-pressure gas refrigerant is sucked into the compressor 21 and compressed to become a high-pressure gas refrigerant. It is sent to the indoor units 40, 50, 60 via the path switching valve 22, the gas side closing valve 27 and the gas refrigerant communication pipe 72. The high-pressure gas refrigerant sent to the indoor units 40, 50, 60 is condensed by exchanging heat with indoor air in the indoor heat exchangers 42, 52, 62, When passing through the indoor expansion valves 41, 51, 61, the pressure is reduced according to the opening degree 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 pipe 71 and further depressurized via the liquid side closing valve 26 and the outdoor expansion valve 38. , Flows into the outdoor heat exchanger 23. The low-pressure gas-liquid two-phase refrigerant flowing into the outdoor heat exchanger 23 exchanges heat with the outdoor air supplied by the outdoor fan 28 to evaporate into a low-pressure gas refrigerant, and passes through the four-way switching valve 22. And flows into the accumulator 24. Then, the low-pressure gas refrigerant that has flowed into the accumulator 24 is again sucked into the compressor 21. In this air conditioner 10, since there is no mechanism for adjusting the refrigerant pressure on the gas side of the indoor heat exchangers 42, 52, 62, the condensation pressure Pc in all the indoor heat exchangers 42, 52, 62 is common. Pressure.

(3) Control of indoor expansion valve by indoor control device (3-1) During cooling In the following, the control during cooling of the indoor expansion valve 41 by the indoor side control device 47 will be mainly described. Control of the indoor expansion valves 51 and 61 by the inner control devices 57 and 67 is also performed. In the control of the indoor expansion valve 41, the indoor control device 47 selects either the first control state during normal operation or the second control state during excessive fluctuation state. In the first control state, for example, the control amount ΔEV of the valve opening degree of the indoor expansion valve 41 follows proportional integral (PI) control, as in the conventional case.

A deviation (= SH1−SHt1) between the current superheat degree SH1 and the target superheat degree SHt1 is expressed as e, the previous deviation is expressed as e _prev, and α and β are constants, and ΔEV = α · (e−e _prev ) + Β · e is determined according to the equation + β · e. The calculation for determining the control amount ΔEV is performed, for example, every time a certain time elapses.

In the second control state, the proportional gain is set larger than that in the first control state. That is, the equation is transformed by multiplying α by a constant γ larger than 1. As a result, the control amount ΔEV used in the second control state is calculated according to the equation: ΔEV = α · γ · (e−e _prev ) + β · e. FIG. 3 is a flowchart showing the determination procedure of the excessive fluctuation state in the operation control device 80 during the cooling operation and the selection procedure for taking the first control state or the second control state. FIG. 4 is a graph showing an example of the relationship between the conventional relative superheat degree RSH1, the target relative superheat degree RSHt1, and the valve opening degree EV when the control is performed only in the first control state. FIG. 5 is a graph showing an example of the relationship between the relative superheat degree RSH1, the target relative superheat degree RSHt1, and the threshold value ε when switching to the second control state. 4 and 5, the solid line represents the relative superheat degree RSH1, and the alternate long and short dash line represents the valve opening degree EV.

  The control of the indoor expansion valve during cooling by the operation control device 80 according to one embodiment will be described with reference to FIGS. 3 to 5. The determination and operation of FIG. 3 are performed for each of the indoor units 40, 50, and 60. In the following description, the indoor unit 40 will be described as an example, and a part of the description of the indoor units 50 and 60 will be omitted. .

  In step S1, the indoor side control devices 47, 57, and 67 determine whether or not the indoor expansion valves 41, 51, and 61 have been determined with the control amount EV by model-based IP control. That is, whether or not the control system of the indoor expansion valves 41, 51, 61 that is the control target is realized using a model that formulates the input / output relationship of the indoor expansion valves 41, 51, 61 that are the control targets. Determine whether. When the control amount ΔEV of the indoor expansion valves 41, 51, 61 is determined by the model base IP control, the process proceeds to the next step S2.

  In step S2, the current refrigerant temperature value (Tg) on the outlet side of the indoor heat exchanger 42 is acquired by the gas side temperature sensor 45, and the current refrigerant temperature on the inlet side of the indoor heat exchanger 42 is acquired by the liquid side temperature sensor 44. A value (Te) is obtained. At the same time, the room temperature (Tr) is acquired by the room temperature sensor 46. The superheat degree SH1 is obtained by subtracting the current refrigerant temperature value (Te) detected by the liquid side temperature sensor 44 from the refrigerant temperature value (Tg) detected by the gas side temperature sensor 45. Further, the relative superheat degree RSH1 is calculated using a relational expression [RSH = SH / (Tr−Te)] of the relative superheat degree RSH1, the superheat degree SH1, the room temperature Tr, and the evaporation temperature Te.

  In step S3, the indoor side control device 47 reads the target relative superheat degree RSHt1 from the memory 47c. A threshold ε to be compared with a value obtained by subtracting the target relative superheat degree RSHt1 from the relative superheat degree RSH1 calculated in step S2 is determined in advance. For example, if the value obtained by subtracting the target relative superheat degree RSHt1 from the relative superheat degree RSH1 is larger than the threshold value ε, the indoor side control device 47 is determined to be in an excessively variable state.

  The first control state continues until time t1 when the deviation between the relative superheat degree RSH1 and the target relative superheat degree RSHt1 exceeds the threshold ε. That is, until the deviation between the relative superheat degree RSH1 and the target relative superheat degree RSHt1 exceeds the threshold value ε, the process returns from step S3 to step S2, and the operations of steps S2 and S3 are repeated thereafter.

  At time t1, unlike the conventional case, the operation control device 80 switches from the first control state to the second control state because the difference between the relative superheat degree RSH1 and the target relative superheat degree RSHt1 exceeds the threshold ε. However, even when the second control state is entered, the operation control device 80 does not immediately shift to the operation state (second operation amount changing operation) in which the proportional gain is increased.

  In step S4, similarly to step S2, the current refrigerant temperature values (Te, Tg) on the outlet side and the inlet side of the indoor heat exchanger 42 acquired by the gas side temperature sensor 45 and the liquid side temperature sensor 44 are used. The degree of superheat SH1 is calculated.

In step S5, the deviation e _{prev of the} superheat calculated previously is compared with the current deviation e derived from the superheat calculated in step S4. Then, it is determined whether or not _{ee prev} <0. This determination is to know the time point (time t2) when the curve of the relative superheat degree RSH1 starts to fall. If the determination in step S5 is made after time t2 when e−e _prev <0, it is determined Yes and the process proceeds to the next step S6. Until time t2, the process returns from step S5 to step S4, and the operations of steps S4 and S5 are repeated until _{ee prev} <0.

In step S6, the operation control device 80 increases the proportional gain, and after time t2, the opening of the indoor expansion valve 41 changes according to the equation: ΔEV = α · γ · (e−e _prev ) + β · e. Therefore, after the time t2, when FIG. 4 is compared with FIG. 5, the change of the valve opening degree EV becomes larger in the graph shown in FIG. Therefore, the time t3 when the relative superheat degree RSH1 in the graph of FIG. 5 reaches the target relative superheat degree RSHt1 is earlier than the time t4 when the relative superheat degree RSH of the graph of FIG. 4 reaches the target relative superheat degree RSHt1. ing.

  At time t6 in FIG. 4 and time t5 in FIG. 5, the relative superheating degree RSH1 is a minimum value, but the state of the refrigerant is worsened in the refrigerant circuit 11 in the case of FIG. Since the degree can be reduced, it is suppressed that the relative superheat RSH1 is greatly decreased from the target value. That is, the value of the relative superheat RSH1 at time t5 in FIG. 5 is larger than the value of the relative superheat RSH1 at time t6 in FIG.

  The determination in step S7 will be described later, and the operations in steps S8 to S11 will be described first. In FIG. 5, the graph of the relative superheat degree RSH1 is the target relative superheat degree RSHt1 at time t7. In step S8, similarly to step S2, the current refrigerant temperature values (Te, Tg) on the outlet side and the inlet side of the indoor heat exchanger 42 acquired by the gas side temperature sensor 45 and the liquid side temperature sensor 44 are used. A relative superheat RSH1 is calculated.

  In step S9, it is determined whether or not the relative superheat degree RSH1 has become smaller than the target relative superheat degree RSHt1 even after the operation to increase the proportional gain. After time t3 in FIG. 5, an undershoot occurs in which the curve of the relative superheat degree RSH1 is lower than the target relative superheat degree RSHt1, and this is stored in the memory 47c of the indoor control device 47, and time t3 Thereafter, it is always determined as “Yes” in step S9 until returning to the first control state.

  However, since the curve of the relative superheat degree RSH1 is below the target relative superheat degree RSHt1 between the time t3 and the time t7 in FIG. 5, the state of RSH1 <RSHt1 is maintained, and RSH1 ≧ RSHt1 in step S10 Judged not. Then, the operations in steps S8 to S10 are repeated, and the indoor side control device 47 waits for the target relative superheat degree RSHt1 to reach the relative superheat degree RSH1.

  When the time t7 shown in FIG. 5 has passed, it is determined in step S10 that the target relative superheat RSHt1 has reached the relative superheat RSH1, and the indoor control device 47 proceeds to the next step S11. . Then, the value of the proportional gain is restored to return to the first control state.

  In step S7, it is determined whether or not the time from time t2 to time t7, that is, the time from when the proportional gain is increased until the value of the proportional gain is returned to the first control state is within 30 minutes. To be judged. If it does not return to the first control state within 30 minutes from time t2, it is forcibly returned to the first control state based on the determination in step S7. In such a case, since there is a high possibility that some trouble has occurred, the operation control device 80 is made to respond to the normal control state by returning to the first control state, which is the normal control state.

(3-2) During heating During heating, control based on the degree of supercooling SC1, SC2, SC3 is performed instead of control based on the degree of superheating SH1, SH2, SH3 performed during cooling. In the following, the control during cooling of the indoor expansion valve 41 by the indoor control device 47 will be described, but the same applies to the control of the indoor expansion valves 51 and 61 by the indoor control devices 57 and 67. In the control of the indoor expansion valve 41, the indoor control device 47 selects either the first control state or the second control state. In the first control state, for example, the control amount ΔEV of the valve opening degree of the indoor expansion valve 41 follows proportional integral (PI) control, as in the conventional case.

If the deviation (= SC1-SCt1) between the current supercooling degree SC1 and the target supercooling degree SCt1 is represented by ew, the previous deviation is represented by ew _prev, and αw and βw are constants, ΔEV = αw · (ew− ew _prev ) + βw · ew, the control amount ΔEV is determined. The calculation for determining the control amount ΔEV is performed, for example, every time a certain time elapses.

Even in the heating operation, the proportional gain is made larger in the second control state than in the first control state. That is, the equation is transformed by multiplying α by a constant γw larger than 1. As a result, the control amount ΔEV used in the second control state is calculated according to the equation: ΔEV = αw · γw · (ew−ew _prev ) + βw · ew. FIG. 6 is a flowchart showing the determination procedure of the excessive fluctuation state in the operation control device 80 during the heating operation and the selection procedure for taking the first control state or the second control state.

  The control of the indoor expansion valve during heating by the operation control device 80 according to one embodiment will be described with reference to FIG. 6 is performed for each of the indoor units 40, 50, and 60. In the following description, the indoor unit 40 will be described as an example, and a part of the description of the indoor units 50 and 60 will be omitted.

  In step S1w, as in step S1, the indoor control devices 47, 57, and 67 determine whether or not the indoor expansion valves 41, 51, and 61 have been determined with the model-based IP control by the model base IP control. When the control amount ΔEV of the indoor expansion valves 41, 51, 61 is determined by the model base IP control, the process proceeds to the next step S2.

  In step S2w, unlike step S2, the discharge pressure Pd of the compressor 21 detected by the discharge pressure sensor 30 is converted into a saturation temperature value corresponding to the condensation temperature Tc, and the liquid side temperature sensor 44 is converted from the saturation temperature value of this refrigerant. , 54, 64 are subtracted from the refrigerant temperature values to obtain the degree of supercooling SC1, SC2, SC3 (examples of current state quantities), respectively. Further, using the relational expression [RSC = SC / (Tc−Tr)] of the relative supercooling degree RSC, the supercooling degree SC, the room temperature Tr, and the condensation temperature Tc, the relative supercooling degrees RSC1, RSC2, and RSC3. Is calculated.

  In step S3w, similarly to step S3, the indoor control device 47 reads the target relative subcooling degree RSCs1 from the memory 47c. A threshold εw to be compared with a value obtained by subtracting the target relative supercooling degree RSCs1 from the relative supercooling degree RSC1 calculated in step S2w is determined in advance. For example, if the value obtained by subtracting the target relative supercooling degree RSCs1 from the relative supercooling degree RSC1 is larger than the threshold value εw, the indoor control device 47 determines that the state is an excessively variable state. Until the deviation between the relative supercooling degree RSC1 and the target supercooling degree RSCs1 exceeds the threshold value εw, the process returns from step S3w to step S2w, and thereafter the operations of steps S2w and S3w are repeated.

  Since the difference between the relative supercooling degree RSC1 and the target relative supercooling degree RSCs1 exceeds the threshold εw, the indoor side control device 47 switches from the first control state to the second control state. However, even if the second control state is entered, the indoor control device 47 does not immediately shift to the operation state (second operation amount changing operation) in which the proportional gain is increased.

In step S4w, the degree of supercooling SC1 is calculated as in step S2w. In step S5, the deviation ew _prev of the supercooling degree calculated last time is compared with the supercooling degree ew calculated in step S4w described above. Then, it is determined whether or not ew−ew _prev <0. This determination is to know the point in time when the curve of the relative supercooling degree RSC1 starts to drop. Until ew−ew _prev <0, the process returns from step S5 to step S4w, and the operations of steps S4w and S5w are repeated until ew−ew _prev <0.

When ew−ew _prev <0, the process proceeds to step S6w, where the indoor control device 47 increases the proportional gain, and the indoor expansion valve 41 is increased according to the equation ΔEV = αw · γw · (ew−ew _prev ) + βw · ew. The opening changes. Therefore, the change in the valve opening degree EV becomes large, and the time until the relative supercooling degree RSC1 reaches the target supercooling degree RSCs1 is shortened. As a result, since the degree to which the refrigerant state deteriorates in the refrigerant circuit 11 can be reduced, the relative supercooling degree RSC1 is prevented from being greatly reduced below the target value.

  The determination in step S7w will be described later, and the operations in steps S8w to S11w will be described first. In step S8w, similarly to step S2w, using the current refrigerant temperature value and the condensation temperature (Te, Tc) on the outlet side of the indoor heat exchanger 42 acquired by the gas side temperature sensor 45 and the liquid side temperature sensor 44, A relative subcooling degree RSC1 is calculated.

  In step S9w, it is determined whether or not the relative supercooling degree RSC1 has once become smaller than the target relative subcooling degree RSCs1 after the operation for increasing the proportional gain. If there is an undershoot that causes the curve of the degree RSC1 to be below, this is stored in the memory 47c of the indoor control device 47, and after that, always returns “Yes” in step S9w until returning to the first control state. To be judged.

  However, in a state where the relative supercooling degree RSC1 is undershooting, the curve of the relative supercooling degree RSC1 is below the target relative supercooling degree RSCs1, so the state of RSC1 <RSCs1 is maintained, and RSC1 is maintained in step S10w. It is determined that ≧ RSCs1 is not satisfied. And the operation of step S8w-S10w is repeated, and the indoor side control apparatus 47 waits until target relative subcooling degree RSCs1 reaches relative subcooling degree RSC1.

  If it is determined in step S10w that the target relative supercooling degree RSCs1 has reached the relative supercooling degree RSC1, the indoor control device 47 advances the processing to the next step S11w. Then, the value of the proportional gain is restored to return to the first control state.

  In step S7w, it is determined whether or not the time period from when the proportional gain is increased to when the proportional gain value is restored to the first control state is within 30 minutes. If it does not return to the first control state within 30 minutes after increasing the proportional gain, it is forcibly returned to the first control state based on the determination in step S7w.

(4) Control of Compressor by Outdoor Control Device (4-1) Cooling In the following, control of the compressor 21 by the outdoor control device 37 during cooling will be described. In the control of the compressor 21, the outdoor side control device 37 selects either the first control state during normal time or the second control state during excessive fluctuation state. In the first control state, for example, the control amount ΔFk of the rotational speed of the compressor 21 follows proportional integral (PI) control, as in the conventional case.

If the deviation (= Teg−Teg) between the current evaporation side saturation pressure equivalent temperature Teg and the target evaporation side saturation pressure equivalent temperature Teg is represented by e, the previous deviation is represented by e _prev, and α1 and β1 are constants, ΔFk The control amount ΔFk is determined according to the equation = α1 · (e−e _prev ) + β1 · e. The calculation for determining the control amount ΔFk is performed, for example, every time a certain time elapses.

In the second control state, the proportional gain is set larger than that in the first control state. That is, the equation is transformed by multiplying α1 by a constant γ1 larger than 1. As a result, the control amount ΔFk used in the second control state is calculated according to the equation: ΔFk = α1 · γ1 · (e−e _prev ) + β1 · e. FIG. 7 is a flowchart showing the determination procedure of the excessive fluctuation state in the operation control device 80 during the cooling operation and the selection procedure for taking the first control state or the second control state. FIG. 8 is a graph showing an example of the relationship among the evaporation side saturation pressure equivalent temperature RSH1, the target evaporation side saturation pressure equivalent temperature Tegt, and the threshold value ε when switching to the second control state.

  The control of the compressor during cooling by the operation control device 80 according to one embodiment will be described with reference to FIGS. 7 and 8.

  In step S21, the outdoor side control device 37 determines whether or not the compressor 21 has determined the control amount Fk by model-based IP control. That is, it is determined whether or not the control system of the compressor 21 that is the control target is realized using a model that formulates the input / output relationship of the compressor 21 that is the control target. When the control amount ΔFk of the compressor 21 is determined by the model base IP control, the process proceeds to the next step S22.

  In step S22, the pressure of the refrigerant on the suction side is detected by the suction pressure sensor 29, and the evaporation side saturation pressure equivalent temperature Teg is calculated.

  In step S23, the outdoor side control device 37 reads the target evaporation side saturated pressure equivalent temperature Tegt from the memory 37b. A threshold value ε1 to be compared with a value obtained by subtracting the evaporation side saturation pressure equivalent temperature Teg calculated in step S2 from the target evaporation side saturation pressure equivalent temperature Tegt is determined in advance. For example, if the value obtained by subtracting the evaporation side saturation pressure equivalent temperature Teg from the target evaporation side saturation pressure equivalent temperature Teg is larger than the threshold value ε1, the outdoor side control device 37 is determined to be in an excessively variable state.

  The first control state continues until time t11 when the deviation between the evaporation side saturation pressure equivalent temperature Teg and the target evaporation side saturation pressure equivalent temperature Teg exceeds the threshold ε1. That is, until the deviation between the evaporation side saturation pressure equivalent temperature Teg and the target evaporation side saturation pressure equivalent temperature Teg exceeds the threshold ε1, the process returns from step S23 to step S22, and thereafter the operations of steps S22 and S23 are repeated.

  At time t11, unlike the conventional case, the operation control device 80 changes from the first control state to the second control state because the difference between the evaporation side saturation pressure equivalent temperature Teg and the target evaporation side saturation pressure equivalent temperature Teg exceeds the threshold ε1. Switch. However, even when the second control state is entered, the operation control device 80 does not immediately shift to the operation state (second operation amount changing operation) in which the proportional gain is increased.

  In step S24, similarly to step S22, the suction pressure sensor 29 detects the refrigerant pressure on the suction side, and the evaporation side saturation pressure equivalent temperature Teg is calculated.

In step S25, the deviation e _prev calculated last time is compared with the current deviation e calculated in step S24 described above. Then, it is determined whether or not _{ee prev} > 0. This determination is to know the time point (time t12) when the curve of the evaporation side saturation pressure equivalent temperature Teg starts to rise. If the determination in step S25 is made after time t12 when e−e _prev > 0, the determination is Yes and the process proceeds to the next step S26. Until time t12, the process returns from step S25 to step S24, and the operations of steps S24 and S25 are repeated until _{ee prev} > 0.

In step S26, the operation control device 80 increases the proportional gain, and after time t12, the control amount ΔFk of the rotational speed of the compressor 21 is determined according to the equation: ΔFk = α1 · γ1 · (e−e _prev ) + β1 · e. Change. Therefore, after time t12, the change in the rotational speed Fk increases. Therefore, the time t13 at which the evaporation side saturation pressure equivalent temperature Teg in the graph of FIG. 8 reaches the target evaporation side saturation pressure equivalent temperature Teg is earlier. In addition, at time t14 in FIG. 8, the evaporation side saturated pressure equivalent temperature Teg is a maximum value, but since the proportional gain is increased, the degree of deterioration of the refrigerant state in the refrigerant circuit 11 can be reduced. Therefore, it is suppressed that the evaporation side saturation pressure equivalent temperature Teg increases more than the target value.

  The determination in step S27 will be described later, and the operations in steps S28 to S31 will be described first. In FIG. 8, the graph of the evaporation side saturation pressure equivalent temperature Teg is the target evaporation side saturation pressure equivalent temperature Teg at time t15. In step S28, similarly to step S22, the pressure of the suction side refrigerant is detected by the suction pressure sensor 29, and the evaporation side saturation pressure equivalent temperature Teg is calculated.

  In step S29, it is determined whether or not the evaporation side saturation pressure equivalent temperature Teg has become larger than the target evaporation side saturation pressure equivalent temperature Teg even after the operation for increasing the proportional gain. After time t13 in FIG. 8, an overshoot occurs in which the curve of the evaporation side saturation pressure equivalent temperature Teg is higher than the target evaporation side saturation pressure equivalent temperature Teg, which is the memory 37b of the outdoor control device 37. From time t13, it is always determined as “Yes” in step S9 until returning to the first control state.

  However, since the curve of the evaporation side saturated pressure equivalent temperature Teg is above the target evaporation side saturation pressure equivalent temperature Teg between the time t13 and the time t15 in FIG. 8, the state of Teg> Teg is maintained, and the step In S30, it is determined that Teg ≦ Teg is not satisfied. Then, the operations of steps S28 to S30 are repeated, and the outdoor control device 37 waits for the target evaporation side saturation pressure equivalent temperature Teg to reach the evaporation side saturation pressure equivalent temperature Teg.

  When time t15 shown in FIG. 8 has passed, it is determined in step S10 that the target evaporation side saturation pressure equivalent temperature Teg has reached the evaporation side saturation pressure equivalent temperature Teg, and the outdoor control device 37 performs the following operation. The process proceeds to step S31. Then, the value of the proportional gain is restored to return to the first control state.

  In step S27, it is determined whether or not the time from the time t12 to the time t15, that is, the time from when the proportional gain is increased until the value of the proportional gain is returned to the first control state is within 10 minutes. To be judged. If it does not return to the first control state within 10 minutes from time t12, it is forcibly returned to the first control state based on the determination in step S27. In such a case, since there is a high possibility that some trouble has occurred, the operation control device 80 is made to respond to the normal control state by returning to the first control state, which is the normal control state.

(4-2) During heating Even in the control of the compressor 21 during heating of the compressor 21 by the outdoor side control device 37, the outdoor control device 37 is in the first control state in the normal state and the second control state in the excessively variable state. Select one of the following. In the first control state, for example, the control amount ΔFk of the rotational speed of the compressor 21 follows proportional integral (PI) control, as in the conventional case.

A deviation (= Tcg−Tcgt) between the current condensation side saturation pressure equivalent temperature Tcg and the target condensation side saturation pressure equivalent temperature Tcgt is represented by e, the previous deviation is represented by e _prev, and α2 and β2 are constants, ΔFk The control amount ΔFk is determined according to the equation = α 2 · (e−e _prev ) + β 2 · e. The calculation for determining the control amount ΔFk is performed, for example, every time a certain time elapses.

That is, during heating, control based on the condensation side saturated pressure equivalent temperature Tcg is performed instead of control based on the evaporation side saturated pressure equivalent temperature Teg performed during cooling. Therefore, since only the evaporation side saturated pressure equivalent temperature Teg in the explanation at the time of cooling described above is replaced with the condensation side saturated pressure equivalent temperature Tcg, the explanation is omitted. For example, in the second control state, the proportional gain is larger than that in the first control state, but α2 is multiplied by a constant γ2 larger than 1, and the equation is modified so that the control amount ΔFk used in the second control state is ΔFk. = Α2 · γ2 · (e−e _prev ) + β2 · e. The condensation side saturated pressure equivalent temperature Tcg is calculated by the discharge pressure sensor 30 from the pressure of the refrigerant on the discharge side of the compressor 21. Further, the target condensation side saturation pressure equivalent temperature Tcgt and the threshold value ε2 are stored in the memory 37b.

(5) Features (5-1)
In the above-described embodiment, the air conditioner 10 (refrigeration apparatus) includes the superheat degree SH, the relative superheat degree RSH, the supercool degree SC, the relative supercool degree RSC, the condensation side saturation pressure equivalent temperature Tcg, or the evaporation side saturation pressure due to disturbance or the like. Excessive fluctuations in which the equivalent temperature Teg (an example of control parameter) fluctuates greatly include superheat degree SH, relative superheat degree RSH, supercooling degree SC, relative supercooling degree RSC, condensation side saturated pressure equivalent temperature Tcg, or evaporation side saturated pressure equivalent temperature. Teg is a target superheat degree SHt, a target relative superheat degree RSHt, a target supercool degree SCt, a target relative supercool degree RSCt, a target condensation side saturation pressure equivalent temperature Tcgt, or a target evaporation side saturation pressure equivalent temperature Teg (an example of a control target value). Depending on whether or not the thresholds ε, εw, ε1, ε2 (predetermined values) or more are away from the outdoor control device 37 or the indoor control devices 47, 57, It is detected in 7 (example of the control device). During such an excessive fluctuation, the outdoor side control device 37 and the indoor side control devices 47, 57, and 67 perform an operation based on a calculation formula for a fluctuation amount in which the proportional gain is increased in the PI control (example of second operation amount changing operation). Is used to change the amount of operation of the indoor expansion valves 41, 51, 61 and the compressor 21 (example of actuator), thereby causing excessive fluctuation to be caused by the superheat degree SH, the relative superheat degree RSH, the supercooling degree SC, and the relative supercooling degree RSC. The condensation side saturation pressure equivalent temperature Tcg or the evaporation side saturation pressure equivalent temperature Teg is the target superheat degree SHt, target relative superheat degree RSHt, target supercooling degree SCt, target relative subcooling degree RSCt, target condensation side saturated pressure equivalent temperature Tcgt or The temperature is brought close to the target evaporation side saturation pressure equivalent temperature Tegt so that the refrigerant circuit 11 can be quickly escaped from an inappropriate state at the time of excessive fluctuation. On the other hand, the outdoor side control device 37 and the indoor side control devices 47, 57, and 67 use an operation based on a normal PI control expression (an example of a first operation amount changing operation) except during an excessive fluctuation, By changing the operation amounts of 51 and 61 and the compressor 21, normal hunting is prevented.

(6) Modification (6-1) Modification 1A
In the above embodiment, the air conditioner in which a plurality of indoor units 40, 50, 60 are connected to one outdoor unit 20 has been described. However, in the present invention, one indoor unit is included in one outdoor unit. It is applicable also to the connected air conditioning apparatus.

(6-2) Modification 1B
In the above embodiment, the case of PI control has been described as an example of the first control state, but other control methods such as PID (proportional integral derivative) control can also be used for the first control state.

(6-3) Modification 1C
In the above embodiment, the indoor expansion valves 41, 51, 61 and the compressor 21 are described as examples of actuators. However, the outdoor fan 28 and the indoor fans 43, 53, 63 are used as actuators in the same manner as the control according to the present invention. Can be applied.

(6-4) Modification 1D
In the above-described embodiment, the control to bring the relative superheat degree and the relative supercooling degree close to the target relative superheat degree and the target relative supercooling degree, which are control target values, is described as a control parameter. As described above, the control of the operation control device 80 according to the above embodiment can be applied even when the control is performed so as to approach the target superheat degree or the target supercooling degree, which are control target values.

(6-5) Modification 1E
In the above embodiment, as shown in FIG. 5, at time t1, the difference between the relative superheat degree RSH1 and the target relative superheat degree RSHt1 exceeds the threshold value ε and the first control state is switched to the second control state. From the time t2 beyond the peak to the time t3, there is no fluctuation (hereinafter referred to as secondary disturbance) in which the relative superheat RSH1 is separated from the target relative superheat RSHt1. However, as shown in FIG. 10, a secondary disturbance occurs between time t21 and time t22 between time t2 and time t3. The period between time t21 and time t22 when this secondary disturbance occurs is a secondary disturbance section. Hereinafter, a control example of the indoor control device that can perform better processing when such a secondary disturbance occurs will be described.

(6-5-1) Control of indoor expansion valve during cooling by indoor side control device When such a secondary disturbance occurs, a control example during cooling of the indoor expansion valve of the indoor side control device is shown in FIG. This will be described with reference to a flowchart. Since steps S1 and S2 in FIG. In step S3, the indoor side control device 47 reads the target relative superheat degree RSH1t from the memory 47c. A threshold ε to be compared with a value obtained by subtracting the target relative superheat degree RSH1t from the relative superheat degree RSH1 calculated in step S2 is determined in advance. For example, if the value obtained by subtracting the target relative superheat degree RSH1t from the relative superheat degree RSH1 is larger than the threshold value ε, it is determined that the indoor control device 47 is in an excessively variable state.

  The first control state continues until time t1 when the deviation between the relative superheat degree RSH1 and the target relative superheat degree RSH1t exceeds the threshold value ε. That is, until the deviation between the relative superheat degree RSH1 and the target relative superheat degree RSH1t exceeds the threshold value ε, the process returns from step S3 to step S2, and the operations of steps S2 and S3 are repeated thereafter.

  At time t1, unlike the conventional case, the operation control device 80 switches from the first control state to the second control state because the difference between the relative superheat degree RSH1 and the target relative superheat degree RSH1t exceeds the threshold ε. However, even when the second control state is entered, the operation control device 80 does not immediately shift to the operation state (second operation amount changing operation) in which the proportional gain is increased.

  In step S4, similarly to step S2, the current refrigerant temperature values (Te, Tg) on the outlet side and the inlet side of the indoor heat exchanger 42 acquired by the gas side temperature sensor 45 and the liquid side temperature sensor 44 are used. The degree of superheat SH1 is calculated.

In step S5, the deviation e _{prev of the} superheat calculated previously is compared with the current deviation e derived from the superheat calculated in step S4. Then, it is determined whether or not _{ee prev} <0. This determination is for determining whether or not the curve of the relative superheat degree RSH1 starts to fall and the relative superheat degree RSH1 moves close to the target relative superheat degree RSH1t. After the time t1, when the determination in step S5 is made in a state where _{ee prev} <0, it is determined Yes and the process proceeds to the second operation amount changing operation in the next step S6A. However, if the determination of step S5 is performed in a state where ee _prev ≧ 0 (the state from time t21 to time t22), it is determined No and the process proceeds to the first operation amount changing operation in the next step S6B. .

In step S6A, the operation control device 80 increases the proportional gain, and the opening degree of the indoor expansion valve 41 changes according to the equation: ΔEV = α · γ · (e−e _prev ) + β · e. Therefore, when FIG. 4 and FIG. 9 are compared after the time t2, the change of the valve opening degree EV becomes larger in the graph shown in FIG. Therefore, the time t3 when the relative superheat degree RSH1 of the graph of FIG. 9 reaches the target relative superheat degree RSH1t is earlier than the time t4 when the relative superheat degree RSH of the graph of FIG. 4 reaches the target relative superheat degree RSH1t. ing.

  At time t6 in FIG. 4 and at time t5 in FIG. 9, the relative superheat degree RSH1 is a minimum value, but the state of the refrigerant in the refrigerant circuit 11 is worse in the case of FIG. 9 in which the proportional gain is increased. Since the degree can be reduced, it is suppressed that the relative superheat RSH1 is greatly decreased from the target value. That is, the value of the relative superheat RSH1 at time t5 in FIG. 9 is larger than the value of the relative superheat RSH1 at time t6 in FIG.

In step S6B, the operation control device 80 does not increase the proportional gain, and the opening degree of the indoor expansion valve 41 changes according to the equation: ΔEV = α · (e−e _prev ) + β · e, as in the first control state. .

  In a location where the curve of the relative superheat RSH1 starts to increase due to secondary disturbances, etc., the proportional gain is not increased, thereby reducing the operation that prevents the relative superheat RSH1 from reaching the target relative superheat RSH1t. And the convergence of the relative superheat degree RSH1 to the target relative superheat degree RSH1t is accelerated.

  The determination in step S7 will be described later, and the operations in steps S8 to S11 will be described first. In FIG. 9, the graph of the relative superheat degree RSH1 is the target relative superheat degree RSH1t at time t7. In step S8, similarly to step S2, the current refrigerant temperature values (Te, Tg) on the outlet side and the inlet side of the indoor heat exchanger 42 acquired by the gas side temperature sensor 45 and the liquid side temperature sensor 44 are used. A relative superheat RSH1 is calculated.

In step S9, it is determined whether or not the relative superheat degree RSH1 has become smaller than the target relative superheat degree RSH1t even after the operation for increasing the proportional gain. Before reaching time t3 in FIG. 9, the relative superheat degree RSH1 is higher than the target relative superheat degree RSH1t. Therefore, “No” is determined in this step S9. Thereafter, Steps S4 to S9 are repeated, and the target relative superheat RSH1t is set to the relative superheat RSH1 while adjusting the proportional gain by proceeding to Step S6A or S6B according to the sign of the superheat deviation ee _prev at that time. Will wait for it to drop. Then, after time t3 in FIG. 9, since an undershoot occurs in which the curve of the relative superheat RSH1 is lower than the target relative superheat RSH1t, this is stored in the memory 47c of the indoor control device 47, and the time After t3, “Yes” is always determined in step S9 until the first control state is restored.

However, since the curve of the relative superheat degree RSH1 is below the target relative superheat degree RSH1t between the time t3 and the time t7 in FIG. 9, the state of RSH1 <RSH1t is maintained, and RSH1 ≧ RSH1t in step S10 Judged not. Then, the operations of steps S4 to S10 are repeated, and the target relative superheat degree RSH1t is adjusted while adjusting the proportional gain by proceeding to step S6A or S6B according to the sign of the superheat degree deviation ee _prev at that time. Will wait for the indoor side control device 47 to reach the relative superheat degree RSH1.

  When time t7 shown in FIG. 9 has passed, it is determined in step S10 that the target relative superheat RSH1t has reached the relative superheat RSH1, and the indoor control device 47 advances the processing to the next step S11. . Then, the value of the proportional gain is restored to return to the first control state.

  In step S7, whether or not the time from switching from the time t1 to the time t7, that is, switching from the second control state to returning the proportional gain value to the first control state is within 30 minutes. Is judged. If it does not return to the first control state within 30 minutes from time t1, it is forcibly returned to the first control state based on the determination in step S7. In such a case, since there is a high possibility that some trouble has occurred, the operation control device 80 is made to respond to the normal control state by returning to the first control state, which is the normal control state.

(6-5-2) Control of indoor expansion valve during heating by indoor side control device As described with reference to the flowchart of FIG. 6, during heating, it is based on the degree of superheating SH1, SH2, SH3 performed during cooling. Control based on the degree of supercooling SC1, SC2, SC3 is performed instead of the control. When a secondary disturbance occurs, it is preferable to perform the control shown in the flowchart of FIG. 11 instead of the control example shown in FIG. The difference between the flow of FIG. 6 during heating and the flow of FIG. 11 is the same as the difference between the flow of FIG. 5 and the flow of FIG. 9 during cooling. That is, when “No” is determined in steps S9w and S10w, the process returns to step S4w. If “No” is determined in step S5w, the proportional gain is returned to the original value in step S6wB, and the process proceeds to step S7w. If “Yes” is determined in step S5w, the proportional gain is increased in step S6wA. Then, the process proceeds to step S7w.

In step S6wA, the operation control device 80 increases the proportional gain, and the opening degree of the indoor expansion valve 41 changes according to the equation: ΔEV = αw · (ew−ew _prev ) + βw · ew. In a portion where the curve of the relative supercooling degree RSC1 starts to increase due to a secondary disturbance or the like, the operation that prevents the relative supercooling degree RSC1 from reaching the target relative supercooling degree RSC1t is reduced by not increasing the proportional gain. As a result, the instability of the control is suppressed and the convergence of the relative supercooling degree RSC1 to the target relative supercooling degree RSC1t is accelerated.

(6-5-3) Control of compressor by outdoor side control device during cooling Room interior based on superheats SH1, SH2 and SH3 performed during cooling by indoor side control device 47 described with reference to the flowchart of FIG. Similar to the control of the expansion valve 41, the compressor 21 can be controlled by the outdoor control device 37. When a secondary disturbance occurs, it is preferable to perform the control shown in the flowchart of FIG. 12 in place of the control example shown in FIG. As shown in FIG. 13, a secondary disturbance occurs between time t121 and time t122 between time t12 and time t13. The flow of FIG. 7 and the flow of FIG. 12 in the outdoor control device 37 are different from the flow of FIG. 5 and the flow of FIG. 9 in the indoor control device 47. That is, when “No” is determined in steps S29 and S30, the process returns to step S24. Then, when “No” is determined in step S25 in the state from time t121 to time t122 in FIG. 13, the proportional gain is returned to the original value in step S26B, and the process proceeds to step S27. In step S25, “Yes” is set. If it is determined, the proportional gain is increased in step S26A and the process proceeds to step S27.

In step S26A, the operation control device 80 increases the proportional gain, and the control amount ΔFk changes according to the equation: ΔFk = α1 · (e−e _prev ) + β1 · e. Where the curve of the evaporation side saturation pressure equivalent temperature Teg starts to decrease due to secondary disturbances, etc., the evaporation side saturation pressure equivalent temperature Teg reaches the target evaporation side saturation pressure equivalent temperature Teg by not increasing the proportional gain. In addition to reducing the instability of the control, the convergence of the evaporation side saturation pressure equivalent temperature Teg to the target evaporation side saturation pressure equivalent temperature Tegt is accelerated.

(6-5-4) Control of Compressor by Outdoor Control Device during Heating Also in control of compressor 21 during heating of compressor 21 by outdoor control device 37, outdoor control device 37 is the first in normal operation. When selecting one of the control state and the second control state at the time of an excessively variable state, it is possible to perform control in consideration of secondary disturbance as in cooling. During heating, control based on the condensation side saturated pressure equivalent temperature Tcg is performed instead of the control based on the evaporation side saturated pressure equivalent temperature Teg performed during cooling. Therefore, since only the evaporation side saturated pressure equivalent temperature Teg in the explanation at the time of cooling described above is replaced with the condensation side saturated pressure equivalent temperature Tcg, the explanation is omitted.

DESCRIPTION OF SYMBOLS 10 Air conditioning apparatus 11 Refrigerant circuit 20 Outdoor unit 21 Compressor 23 Outdoor heat exchanger 28 Outdoor fan 29 Suction pressure sensor 30 Discharge pressure sensor 37 Outdoor control device 40, 50, 60 Indoor unit 41, 51, 61 Indoor expansion valve 42 , 52, 62 Indoor heat exchangers 43, 53, 63 Indoor fans 44, 54, 64 Liquid side temperature sensors 45, 55, 65 Gas side temperature sensors 46, 56, 66 Indoor temperature sensors 47, 57, 67 Indoor side control devices 80 Operation control device

JP-A-5-10603

Claims (6)

Refrigerant circuit (11) having an actuator (21, 28, 41, 43, 51, 53, 61, 63) and adjusting the state change of the refrigerant in the vapor compression refrigeration cycle performed by circulating the refrigerant by the actuator When,
Sensors (29, 30, 44, 45, 46, 54, 55, 56) that are attached to the refrigerant circuit, detect the state quantity of the refrigerant related to the state change of the refrigerant in the refrigeration cycle, and output the current state quantity. , 64, 65, 66),
Proportional integral control or proportional integral having a proportional term proportional to the deviation and an integral term proportional to the integral of the deviation so that the control parameter calculated from the current state quantity approaches the control target value A control device (37, 47, 57, 67) to be changed by differential control ;
With
The control device is configured to be capable of switching between a first operation amount changing operation and a second operation amount changing operation having a proportional gain larger than a proportional gain of the first operation amount changing operation with respect to the operation amount changing operation. When an excessive variation in which the deviation between the control target value and the control parameter exceeds a threshold is not detected, the first operation amount changing operation is used. In the excessive variation, the control parameter is set to the control target value. A refrigeration apparatus that switches from the first operation amount changing operation to the second operation amount changing operation when approaching . The control device determines that the excessive fluctuation has occurred and switches the first operation amount change operation to the second operation amount change operation when the control parameter is approaching the control target value, and then performs the control. When the parameter changes in a direction away from the control target value, the second operation amount changing operation is returned to the first operation amount changing operation.
The refrigeration apparatus according to claim 1 . The control device, after switching to the second operation amount change operation, determines that the excessive fluctuation has ended when the control parameter exceeds the control target value and then reaches the control target value,
Switching from the second operation amount changing operation to the first operation amount changing operation when it is determined that the excessive fluctuation has ended,
The refrigeration apparatus according to claim 1 or 2 . The control device forcibly switches from the second operation amount changing operation to the first operation by judging from an elapsed time after switching to the second operation amount changing operation after switching to the second operation amount changing operation. Switch to volume change operation,
The refrigeration apparatus according to claim 1 or 2 . The refrigerant circuit includes a compressor that compresses the refrigerant, a heat source side heat exchanger and a use side heat exchanger that perform heat exchange with the refrigerant, a heat source side fan that blows air to the heat source side heat exchanger, and the use side A use-side fan that blows air to the heat exchanger, and a decompression mechanism that can adjust the decompression of the refrigerant by a valve opening, and the actuator includes the compressor, the heat-source-side fan, the use-side fan, and the decompression mechanism Including at least one of
The refrigeration apparatus according to any one of claims 1 to 4 . A refrigerant circuit that has an actuator and adjusts the state change of the refrigerant in the vapor compression refrigeration cycle performed by circulating the refrigerant by the actuator, and is attached to the refrigerant circuit and relates to the state change of the refrigerant in the refrigeration cycle A sensor that detects the state quantity of the refrigerant to be output and outputs the current state quantity, and is proportional to the deviation of the operation amount of the actuator so that the control parameter calculated from the current state quantity approaches the control target value. A control method of a refrigeration apparatus that is changed by proportional integral control or proportional integral derivative control having a term and an integral term proportional to the integral of the deviation ,
A fluctuation detecting step for detecting an excessive fluctuation in which the deviation between the control target value and the control parameter exceeds a threshold ;
When the excessive fluctuation in which the deviation between the control target value and the control parameter exceeds a threshold is not detected, the first operation amount changing operation is used. In the excessive fluctuation, the control parameter is set to the control target value. An operation changing step of switching from the first operation amount changing operation to a second operation amount changing operation having a proportional gain larger than the proportional gain of the first operation amount changing operation when approaching ;
A method for controlling a refrigeration apparatus.

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