AU2008272365A1

AU2008272365A1 - Refrigeration apparatus

Info

Publication number: AU2008272365A1
Application number: AU2008272365A
Authority: AU
Inventors: Shinichi Kasahara
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2007-06-29
Filing date: 2008-06-11
Publication date: 2009-01-08
Anticipated expiration: 2028-06-11
Also published as: AU2008272365B2; ES2784013T3; CN101688700A; CN101688700B; JP2009014210A; US20100175400A1; EP2175212B1; EP2175212A4; KR20100036345A; WO2009004761A1; EP2175212A1

Description

DESCRIPTION REFRIGERATION APPARATUS TECHNICAL FIELD 5 , The present disclosure relates to a refrigeration apparatus including a refrigerant circuit for performing a supercritical refrigeration cycle. BACKGROUND ART In general, a capability of a refrigeration apparatus including a refrigerant circuit sequentially connecting a compression mechanism, a heat source side heat exchanger, an 10 expansion mechanism, and a utilization side heat exchanger is controlled by controlling the compression mechanism and the expansion mechanism. Patent Document I shows an example of the refrigeration apparatus. The refrigeration apparatus of the Patent Document 1 includes a compressor capacity controller for controlling the capacity of a compressor as the compression 15 mechanism, and an expansion valve controller for controlling the degree of opening of an expansion valve as the expansion mechanism. The compressor capacity controller controls the capacity of the compressor based on a low pressure of a refrigerant flowing in the refrigerant circuit. The expansion valve controller controls the degree of opening of the expansion valve based on the temperature of the refrigerant at an outlet of an evaporator. 20 Then, a control amount of the expansion valve controller is corrected based on the capacity of the compressor. CITATION LIST PATENT DOCUMENT 1: Japanese Patent Publication No. 2002-22242 SUMMARY OF THE DISCLOSURE 25 TECHNICAL PROBLEM D08WB 148 Even if the refrigeration apparatus is configured to correct the control amount of the degree of opening of the expansion valve controlled by the expansion valve controller based on the capacity of the compressor, change of the degree of opening of the expansion valve leads to change of a circulation state of the refrigerant, thereby changing the low pressure of 5 the refrigerant. In response to the change of the low pressure of the refrigerant, the compressor capacity controller adjusts the capacity of the compression mechanism. The change of the capacity of the compressor involves re-correction of the control amount of the expansion valve controller. Thus, a sequence of the correction of the control amount of the expansion valve controller, the change of the low pressure of the refrigerant, the change of the 10 capacity of the compressor, and the re-correction of the control amount of the expansion valve controller occurs in a loop. The control of the low pressure by the compressor, and the control of the degree of superheat by the expansion valve cannot be easily settled. In particular, a refrigeration apparatus for performing a supercritical refrigeration cycle in which a high pressure of the refrigerant is equal to or higher than a critical pressure 15 has a problem of difficulty in settling the control. From this point of view, the present disclosure is intended to allow for improved settling of the control of the capability of a refrigeration apparatus for performing the supercritical refrigeration cycle. SOLUTION TO THE PROBLEM 20 The present disclosure has been achieved by paying attention to a large variation of enthalpy of the refrigerant at an outlet of a gas cooler relative to the change of the high pressure of the supercritical refrigeration cycle. Specifically, in cooling operation in the supercritical refrigeration cycle, the enthalpy of the refrigerant at the outlet of the gas cooler may greatly vary when the high pressure changes due to change of the low pressure. This 25 leads to an event that is not caused by a subcritical refrigerant, i.e., the enthalpy of the 2 D08WB148 refrigerant at an inlet of an indoor heat exchanger varies, thereby changing the degree of superheat of the refrigerant at an outlet of the indoor heat exchanger. As a result, the difficulty of settling of the control increases. Also in heating operation, the enthalpy of the refrigerant at the outlet of the gas cooler may greatly vary due to the change of the high 5 pressure. This leads to great fluctuation of indoor air heating capability, thereby changing the temperature of the indoor air, and changing a target value of the temperature of the refrigerant at the outlet of the gas cooler. This vicious circle further increases the difficulty of settling of the control. Moreover, C0 2 , which is a supercritical refrigerant, shows greater variation in refrigerant density when it is superheated as compared with chlorofluorocarbons 10 (e.g., when an evaporating temperature is 5*C, and the degree of superheat varies from 0*C to 5*C, R41OA shows a decrease in gas density of only 3.5 %, whereas CO 2 shows a decrease of as much as 6.5 %). Further, the supercritical refrigerant shows great variation in circulating amount and capability of the apparatus due to the change of the degree of superheat, thereby greatly affecting the controllability. In view of this, the present disclosure is intended to 15 control the high pressure of the refrigeration cycle, and a predetermined physical value controlled by the control of the capability of the apparatus in a concurrent manner. A first aspect of the disclosure is directed to a refrigeration apparatus including: a refrigerant circuit (20) sequentially connecting a compression mechanism (21), a heat source side heat exchanger (23), an expansion mechanism (24), and a utilization side heat exchanger 20 (27), and performing a supercritical refrigeration cycle in which a high pressure is a supercritical pressure of a refrigerant or higher; and a control section (40) for controlling a plurality of objects of control including at least the compression mechanism (21) and the expansion mechanism (24). The control section (40) concurrently controls the plurality of objects of control, thereby concurrently controlling a predetermined physical value of the 25 refrigeration apparatus, and the high pressure of the refrigeration cycle. 3 D08WBl48 With this configuration, the predetermined physical value is controlled, while controlling the high pressure of the refrigeration cycle in the refrigerant circuit (20). Specifically, a different physical value can be controlled in consideration of the change of the high pressure of the refrigeration cycle, and the change of enthalpy of the refrigerant at an 5 outlet of a gas cooler, due to adjustment of the objects of control. In this way, the plurality of objects of control are concurrently controlled so as to concurrently control the high pressure of the refrigeration cycle and the predetermined physical value, thereby controlling the objects of control by taking into account the effect of their changes on the high pressure and the predetermined physical value. Therefore, an event can be avoided in which the 10 objects of control are independently controlled, and the corresponding high pressure of the refrigeration cycle and predetermined physical value are independently changed, and are affected by each other, thereby resulting in difficulty in settling the control. This allows for an improved convergence rate of the control of the predetermined physical value and the high pressure in the refrigeration apparatus. 15 In a second aspect of the disclosure related to the first aspect of the disclosure, the control section (40) receives the predetermined physical value, and the high pressure of the refrigeration cycle as inputs, generates control signals each corresponding to the plurality of objects of control by associating the physical value and the high pressure with each other, and outputs the control signals to the corresponding objects of control, respectively, thereby 20 concurrently controlling the predetermined physical value, and the high pressure of the refrigeration cycle. With this configuration, the control signals for controlling the plurality of objects of control, respectively, are generated by associating the input predetermined physical value and high pressure of the refrigeration cycle with each other. This allows for controlling the 25 objects of control by taking both of the predetermined physical value and the high pressure 4 D08WB148 into consideration, instead of controlling the objects of control by inputting any one of the predetermined physical value and the high pressure. Since the plurality of objects of control are concurrently controlled as described above, a control signal for one of the objects of control can be generated in consideration of the effect of adjustment of the other objects of 5 control on the predetermined physical value and the high pressure. In a third aspect of the disclosure related to the first or second aspect of the disclosure, the refrigeration apparatus further includes: a heat source side fan (28) for feeding air to the heat source side heat exchanger (23) in which the refrigerant exchanges heat with the air, wherein in cooling operation, the predetermined physical value includes an 10 evaporating temperature of the refrigerant in the utilization side heat exchanger (27), and a degree of superheat of the refrigerant at an outlet of the utilization side heat exchanger (27), the objects of control further include the heat source side fan (28), and the control section (40) receives the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the high pressure of the refrigeration cycle as inputs, and concurrently 15 controls the compression mechanism (21), the expansion mechanism (24), and the heat source side fan (28), thereby concurrently controlling the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the high pressure of the refrigeration cycle. With this configuration, in the cooling operation, three objects of control, i.e., the compression mechanism (21), the expansion mechanism (24), and the heat source side fan 20 (28), are concurrently controlled, thereby concurrently controlling the high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, and the degree of superheat of the refrigerant. Thus, the evaporating temperature and the degree of superheat of the refrigerant can be controlled with the high pressure of the refrigeration cycle stably controlled to a desired target value. This allows for an improved convergence rate of the control of the 25 high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, and the 5 D08WB148 degree of superheat of the refrigerant. In a fourth aspect of the disclosure related to the first or second aspect of the disclosure, in heating operation, the predetermined physical value includes a degree of superheat of the refrigerant at an outlet of the heat source side heat exchanger (23), and the 5 control section (40) receives the degree of superheat of the refrigerant, and the high pressure of the refrigeration cycle as inputs, and concurrently controls the compression mechanism (21) and the expansion mechanism (24), thereby concurrently controlling the degree of superheat of the refrigerant, and the high pressure of the refrigeration cycle. With this configuration, in the heating operation, two objects of control, i.e., the 10 compression mechanism (21) and the expansion mechanism (24), are concurrently controlled, thereby concurrently controlling the high pressure of the refrigeration cycle, and the degree of superheat of the refrigerant. Thus, the degree of superheat of the refrigerant can be controlled with the high pressure of the refrigeration cycle stably controlled to a desired target value. This allows for an improved convergence rate of the control of the high pressure of 15 the refrigeration cycle, and the degree of superheat of the refrigerant. In a fifth aspect of the disclosure related to the first or second disclosure, the compression mechanism includes a first compressor (21 a) for sucking and compressing a low pressure refrigerant, and a second compressor (21b) for further compressing and discharging the refrigerant discharged from the first compressor (21a), the expansion mechanism includes 20 a first expansion mechanism (24) for expanding a high pressure refrigerant, and a second expansion mechanism (26) for further expanding the refrigerant expanded to an intermediate pressure refrigerant by the first expansion mechanism (24). In cooling operation, the predetermined physical value includes an evaporating temperature of the refrigerant in the utilization side heat exchanger (27), a degree of superheat of the refrigerant at an outlet of the 25 utilization side heat exchanger (27), and an intermediate pressure of the refrigeration cycle, 6 D08WB148 and the control section (240) receives the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, the intermediate pressure of the refrigeration cycle, and the high pressure of the refrigeration cycle as inputs, and concurrently controls the first and second compressors (21a, 21b), and the first and second expansion mechanisms (24, 26), 5 thereby concurrently controlling the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, the intermediate pressure of the refrigeration cycle, and the high pressure of the refrigeration cycle. With this configuration, in the cooling operation, four objects of control, i.e., the first and second compressors (2 1a, 21b), and the first and second expansion mechanisms (24, 10 26), are concurrently controlled, thereby concurrently controlling the high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the intermediate pressure. Thus, the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the intermediate pressure of the refrigeration cycle can be controlled with the high pressure of the refrigeration cycle stably 15 controlled to a desired target value. This allows for an improved convergence rate of the control of the high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the intermediate pressure of the refrigeration cycle. In a sixth aspect of the disclosure related to the first or second aspect of the 20 disclosure, the compression mechanism includes a first compressor (21a) for sucking and compressing a low pressure refrigerant, and a second compressor (21b) for further compressing and discharging the refrigerant discharged from the first compressor (21a), the expansion mechanism includes a first expansion mechanism (24) for expanding a high pressure refrigerant, and a second expansion mechanism (26) for further expanding the 25 refrigerant expanded to an intermediate pressure refrigerant in the first expansion mechanism 7 D08WB148 (24). In heating operation, the predetermined physical value includes an evaporating temperature of the refrigerant in the heat source side heat exchanger (23), a degree of superheat of the refrigerant at an outlet of the heat source side heat exchanger (23), and a gas cooler outlet temperature which is a temperature of the refrigerant at an outlet of the 5 utilization side heat exchanger (27), and the control section (240) receives the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, the gas cooler outlet temperature of the refrigerant, and the high pressure of the refrigeration cycle as inputs, and concurrently controls the first and second compressors (21a, 21b), and the first and second expansion mechanisms (24, 26), thereby concurrently controlling the evaporating temperature 10 of the refrigerant, the degree of superheat of the refrigerant, the gas cooler outlet temperature of the refrigerant, and the high pressure of the refrigeration cycle. With this configuration, in the heating operation, four objects of control, i.e., the first and second compressors (21 a, 21 b), and the first and second expansion mechanisms (24, 26), are concurrently controlled, thereby concurrently controlling the high pressure of the 15 refrigeration cycle, the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the gas cooler outlet temperature. Thus, the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the gas cooler outlet temperature can be controlled with the high pressure of the refrigeration cycle stably controlled to a desired target value. This allows for an improved convergence rate of the 20 control of the high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the gas cooler outlet temperature. In a seventh aspect of the disclosure related to the first or second aspect of the disclosure, a plurality ones of the utilization side heat exchanger (27a, 27b) are connected in parallel with each other, the expansion mechanism includes a plurality of utilization side 25 expansion mechanisms (26a, 26b) each corresponding to the utilization side heat exchangers 8 D08WB148 (27a, 27b), and a heat source side expansion mechanism (24) provided between the utilization side heat exchangers (27a, 27b) and expansion mechanisms (26a, 26b), and the heat source side heat exchanger (23). In cooling operation, the predetermined physical value includes evaporating temperatures of the refrigerant in the utilization side heat exchangers (27a, 27b), 5 and degrees of superheat of the refrigerant at outlets of the utilization side heat exchangers (27a, 27b), and the control section (340) receives the evaporating temperatures of the refrigerant, the degrees of superheat of the refrigerant in the utilization side heat exchangers (27a, 27b), and the high pressure of the refrigeration cycle as inputs, and concurrently controls the compression mechanism (21), the plurality of utilization side heat expansion 10 mechanisms (26a, 26b), and the heat source side expansion mechanism (24), thereby concurrently controlling the evaporating temperatures of the refrigerant, and the degrees of superheat of the refrigerant in the utilization side heat exchangers (27a, 27b), and the high pressure of the refrigeration cycle. With this configuration, in the cooling operation, a plurality of objects of control, 15 i.e., the compression mechanism (21), the heat source side expansion mechanism (24), and the plurality of utilization side expansion mechanisms (26a, 26b), are concurrently controlled, thereby concurrently controlling the high pressure of the refrigeration cycle, and the evaporating temperatures of the refrigerant, and the degrees of superheat of the refrigerant at the utilization side heat exchangers (27a, 27b). Thus, the evaporating temperatures of the 20 refrigerant, and the degrees of superheat of the refrigerant at the utilization side heat exchangers (27a, 27b) can be controlled with the high pressure of the refrigeration cycle stably controlled to a desired target value. This allows for an improved convergence rate of the control the high pressure of the refrigeration cycle, the evaporating temperatures of the refrigerant, and the degrees of superheat of the refrigerant at the utilization side heat 25 exchangers (27a, 27b). 9 D08WB 148 In an eighth aspect of the disclosure related to the first or second aspect of the disclosure, a plurality ones of the utilization side heat exchanger (27a, 27b) are connected in parallel with each other, the expansion mechanism includes a plurality of utilization side expansion mechanisms (26a, 26b) each corresponding to the utilization side heat exchangers 5 (27a, 27b), and a heat source side expansion mechanism (24) provided between the utilization side heat exchangers (27a, 27b) and expansion mechanisms (26a, 26b), and the heat source side heat exchanger (23). In heating operation, the predetermined physical value includes a degree of superheat of the refrigerant at an outlet of the heat source side heat exchanger (23), and gas cooler outlet temperatures of the refrigerant which are temperatures of the refrigerant 10 at outlets of the utilization side heat exchangers (27a, 27b), and the control section (340) receives the degree of superheat of the refrigerant, the gas cooler outlet temperatures of the refrigerant in the utilization side heat exchangers (27a, 27b), and the high pressure of the refrigeration cycle as inputs, and concurrently controls the compression mechanism (21), the plurality of utilization side expansion mechanisms (26a, 26b), and the heat source side 15 expansion mechanism (24), thereby concurrently controlling the degree of superheat of the refrigerant, the gas cooler outlet temperatures of the refrigerant in the utilization side heat exchangers (27a, 27b), and the high pressure of the refrigeration cycle. With this configuration, in the heating operation, a plurality of objects of control, i.e., the compression mechanism (21), the heat source side expansion mechanism (24), and the 20 plurality of utilization side expansion mechanisms (26a, 26b), are concurrently controlled, thereby concurrently controlling the high pressure of the refrigeration cycle, the degree of superheat of the refrigerant, and the gas cooler outlet temperatures at the utilization side heat exchangers (27a, 27b). Thus, the degree of superheat of the refrigerant, and the gas cooler outlet temperatures of the refrigerant at the utilization side heat exchangers (27a, 27b) can be 25 controlled with the high pressure of the refrigeration cycle stably controlled to a desired target 10 D08WB148 value. This allows for an improved convergence rate of the control of the high pressure of the refrigeration cycle, the degree of superheat of the refrigerant, and the gas cooler outlet temperatures of the refrigerant at the utilization side heat exchangers (27a, 27b). ADVANTAGES OF THE DISCLOSURE 5 According to the present disclosure, a plurality of objects of control are concurrently controlled, thereby concurrently controlling the predetermined physical value of the refrigeration apparatus, and the high pressure of the refrigeration cycle. Therefore, the predetermined physical value, and the high pressure of the refrigeration cycle can be controlled concurrently while concurrently considering the predetermined physical value and 10 the high pressure of the refrigeration cycle, and considering the effect of the plurality of objects of control on the predetermined physical value and the high pressure of the refrigeration cycle. This allows for an improved convergence rate of the control of the predetermined physical value and the high pressure of the refrigeration apparatus. According to the second aspect of the disclosure, the control signals for controlling 15 the plurality of objects of control, respectively, are generated by associating the input predetermined physical value and high pressure of the refrigeration cycle with each other. Therefore, a control signal for one of the objects of control can be generated in concurrent consideration of the predetermined physical value and the high pressure, and in consideration of the effect of adjustment of the other objects of control on the predetermined physical value 20 and the high pressure. This allows for an improved convergence rate of the control of the predetermined physical value and the high pressure of the refrigeration apparatus. According to the third aspect of the disclosure, three objects of control, i.e., the compression mechanism (21), the expansion mechanism (24), and the heat source side fan (28), are concurrently controlled in the cooling operation, thereby concurrently controlling the 25 high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, and the I I D08WB148 degree of superheat of the refrigerant. This allows for an improved convergence rate of the control of the high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, and the degree of superheat of the refrigerant. According to the fourth aspect of the disclosure, two objects of control, i.e., the 5 compression mechanism (21) and the expansion mechanism (24), are concurrently controlled in the heating operation, thereby concurrently controlling the high pressure of the refrigeration cycle, and the degree of superheat of the refrigerant. This allows for an improved convergence rate of the control of the high pressure of the refrigeration cycle, and the degree of superheat of the refrigerant. 10 According to the fifth aspect of the disclosure, four objects of control, i.e., the first and second compressors (21 a, 21b), and the first and second expansion mechanisms (24, 26), are concurrently controlled in the cooling operation in the refrigeration apparatus for performing a two-stage compression refrigeration cycle, thereby concurrently controlling the high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, the 15 degree of superheat of the refrigerant, and the intermediate pressure of the refrigeration cycle. This allows for an improved convergence rate of the control of the high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the intermediate pressure of the refrigeration cycle. According to the sixth aspect of the disclosure, four objects of control, i.e., the first 20 and second compressors (21a, 21b), and the first and second expansion mechanisms (24, 26), are concurrently controlled in the heating operation in the refrigeration apparatus for performing the two-stage compression refrigeration cycle, thereby concurrently controlling the high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the gas cooler outlet temperature. This allows for 25 an improved convergence rate of the control of the high pressure of the refrigeration cycle, the 12 D08WBl48 evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the gas cooler outlet temperature. According to the seventh aspect of the disclosure, a plurality of objects of control, i.e., the compression mechanism (21), the heat source side expansion mechanism (24), and a 5 plurality of utilization side expansion mechanisms (26a, 26b), are concurrently controlled in the cooling operation of a so-called multi-type refrigeration apparatus including a plurality of indoor units, thereby concurrently controlling the high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, and the degrees of superheat at the heat utilization side heat exchangers (27a, 27b). This allows for an improved convergence rate of the 10 control of the high pressure of the refrigeration cycle, the evaporating temperature of the refrigerant, and the degrees of superheat in the utilization side heat exchangers (27a, 27b). According to the eighth aspect of the disclosure, a plurality of objects of control, i.e., the compression mechanism (21), the heat source side expansion mechanism (24), and a plurality of utilization side expansion mechanisms (26a, 26b), are concurrently controlled in 15 the heating operation in the so-called multi-type refrigeration apparatus including a plurality of indoor units, thereby concurrently controlling the high pressure of the refrigeration cycle, the degree of superheat of the refrigerant, and the gas cooler outlet temperatures of the refrigerant at the utilization side heat exchangers (27a, 27b). This allows for an improved convergence rate of the control of the high pressure of the refrigeration cycle, the degree of 20 superheat of the refrigerant, and the gas cooler outlet temperatures of the refrigerant in the utilization side heat exchangers (27a, 27b). BRIEF DESCRIPTION OF THE DRAWINGS [FIG. 1] FIG. 1 is a piping diagram illustrating the structure of an air conditioner of a first embodiment. 25 [FIG. 2] FIG. 2 is a control block diagram of a controller in cooling operation. 13 D08WB 148 [FIG. 3] FIG. 3 is a control block diagram of the controller in heating operation. [FIG. 4] FIG. 4 is a piping diagram illustrating the structure of an air conditioner of a second embodiment. [FIG. 5] FIG. 5 is a control block diagram of a controller in cooling operation. 5 [FIG. 6] FIG. 6 is a control block diagram of the controller in heating operation. [FIG. 7] FIG. 7 is a piping diagram illustrating the structure of an air conditioner of a third embodiment. [FIG. 8] FIG. 8 is a control block diagram of a controller in cooling operation. [FIG. 9] FIG. 9 is a control block diagram of the controller in heating operation. 10 [FIG. 10] FIG. 10 is a piping diagram illustrating the structure of an air conditioner of another embodiment. [FIG. 11] FIG. 11 is a piping diagram illustrating the structure of an air conditioner of still another embodiment. DESCRIPTION OF EMBODIMENTS 15 Embodiments of the present disclosure will be described in detail with reference to the drawings. [First Embodiment] A first embodiment of the present disclosure will be described in detail with reference to the drawings. 20 As shown in FIG. 1, an air conditioner (10) of the present embodiment includes a refrigerant circuit (20), and a controller (40). The refrigerant circuit (20) is a closed circuit filled with carbon dioxide (CO 2 ) as a refrigerant. The refrigerant circuit (20) is configured to perform a vapor compression refrigeration cycle by circulating the refrigerant. Further, the refrigerant circuit (20) is 25 configured to perform a supercritical refrigeration cycle in which a high pressure is equal to or 14 D08WB148 higher than a supercritical pressure of carbon dioxide (i.e., a refrigeration cycle in which a vapor pressure is equal to or higher than a supercritical temperature of carbon dioxide). The refrigerant circuit (20) connects a compressor (21), a four way switching valve (22), an outdoor heat exchanger (23), an outdoor expansion valve (24), and an indoor heat 5 exchanger (27). Specifically, in the refrigerant circuit (20), a discharge side of the compressor (21) is connected to a first port of the four way switching valve (22), and a suction side of the compressor (21) is connected to a second port of the four way switching valve (22). In the refrigerant circuit (20), the outdoor heat exchanger (23), the outdoor expansion valve (24), 10 and the indoor heat exchanger (27) are sequentially arranged in a path from a third port to a fourth port of the four way switching valve (22). The compressor (21) is configured as a fully sealed variable capacity compressor. The compressor (21) sucks and compresses the refrigerant (carbon dioxide) to a supercritical pressure or higher, and then discharges the compressed refrigerant. Changing a frequency of 15 AC fed to a motor (not shown) of the compressor (21) changes a rotation speed, i.e., a capacity, of the compressor (21). The compressor (21) constitutes a compression mechanism. In the outdoor heat exchanger (23), outdoor air sucked by an outdoor fan (28) exchanges heat with the refrigerant. In the indoor heat exchanger (27), indoor air sucked by 20 an indoor fan (29) exchanges heat with the refrigerant. The outdoor heat exchanger (23) constitutes a heat source side heat exchanger, and the indoor heat exchanger (27) constitutes a utilization side heat exchanger. The outdoor fan (28) constitutes a heat source side fan. The outdoor expansion valve (24) is comprised of an electronic expansion valve whose degree of opening is variable, and whose valve element (not shown) is driven by a 25 pulse motor (not shown). The outdoor expansion valve (24) constitutes an expansion 15 D08WB 148 mechanism. The four way switching valve (22) is switchable between a first state where the first and third ports communicate with each other, and the second and fourth ports communicate with each other (a state indicated by a solid line in FIG. 1), and a second state where the first 5 and fourth ports communicate with each other, and the second and third ports communicate with each other (a state indicated by a broken line in FIG. 1). Thus, the air conditioner (10) is able to switchably perform cooling operation and heating operation by switching the four way switching valve (22). In the cooling operation, the four way switching valve (22) is set to the first state. 10 When the compressor (21) is operated in this state, the outdoor heat exchanger (23) functions as a radiator (a gas cooler), and the indoor heat exchanger (27) functions as an evaporator to perform the refrigeration cycle. Specifically, the refrigerant in the supercritical state discharged from the compressor (21) flows into the outdoor heat exchanger (23), and dissipates heat to the outdoor air. After the heat dissipation, the refrigerant expands 15 (decreases in pressure) as it passes through the outdoor expansion valve (24), and then flows into the indoor heat exchanger (27). The refrigerant in the indoor heat exchanger (27) absorbs heat from the indoor air to evaporate, and the cooled indoor air is fed to the inside of the room. The evaporated refrigerant is sucked into and compressed in the compressor (21). In the heating operation, the four way switching valve (22) is set to the second state. 20 When the compressor (21) is operated in this state, the indoor heat exchanger (27) functions as a radiator (a gas cooler), and the outdoor heat exchanger (23) functions as an evaporator to perform the refrigeration cycle. Specifically, the refrigerant in the supercritical state discharged from the compressor (21) flows into the indoor heat exchanger (27), and dissipates heat to the indoor air. The heated indoor air is fed to the inside of the room. After the heat 25 dissipation, the refrigerant expands (decreases in pressure) as it passes through the outdoor 16 D08WB148 expansion valve (24). The refrigerant expanded by the outdoor expansion valve (24) flows into the outdoor heat exchanger (23), and absorbs heat from the outdoor air to evaporate. The evaporated refrigerant is sucked into and compressed in the compressor (21). In the air conditioner (10) configured in this manner, the refrigerant circuit (20) 5 includes an outdoor temperature sensor (30), an indoor temperature sensor (31), a low pressure sensor (32), a discharge temperature sensor (33), a high pressure sensor (34), a gas cooler outlet temperature sensor (37) for the heating operation, and a gas cooler outlet temperature sensor (39) for the cooling operation. The outdoor temperature sensor (30) is a temperature sensing part for sensing the 10 temperature of the outdoor air entering the outdoor heat exchanger (23). The indoor temperature sensor (31) is a temperature sensing part for sensing the temperature of the indoor air entering the indoor heat exchanger (27). The low pressure sensor (32) is a pressure sensing part for sensing the pressure of the refrigerant sucked into the compressor (21), i.e., the low pressure of the refrigeration cycle in the refrigerant circuit (20). The discharge 15 temperature sensor (33) is a temperature sensing part for sensing the temperature of the refrigerant discharged from the compressor (21). The high pressure sensor (34) is a pressure sensing part for sensing the pressure of the refrigerant discharged from the compressor (21), i.e., the high pressure of the refrigeration cycle in the refrigerant circuit (20). The gas cooler outlet temperature sensor (37) for the heating operation is a temperature sensing part for 20 sensing the temperature of the refrigerant at an outlet of the indoor heat exchanger (27) when the refrigerant circulates in the refrigerant circuit (20) in a heating cycle. The gas cooler outlet temperature sensor (39) for the cooling operation is a temperature sensing part for sensing the temperature of the refrigerant at an outlet of the outdoor heat exchanger (23) when the refrigerant circulates in the refrigerant circuit (20) in a cooling cycle. 25 The controller (40) is configured to receive output signals from the indoor 17 D08WBl48 temperature sensor (31), the low pressure sensor (32), the discharge temperature sensor (33), and the high pressure sensor (34), and to control an operation frequency of the compressor (21), the degree of opening of the outdoor expansion valve (24), and an operation frequency of the outdoor fan (28). The controller (40) functions as a control section. 5 The controller (40) includes, as shown in FIGS. 2 and 3, a target low pressure calculator (41) for calculating a target low pressure Pls which is a target value of the low pressure of the refrigeration cycle, a target high pressure calculator (42) for calculating a target high pressure Phs which is a target value of the high pressure of the refrigeration cycle, a target discharge temperature calculator (43) for calculating a target discharge temperature 10 Tls which is a target value of the discharge temperature of the refrigerant, and a control signal generator (49) for generating control signals transmitted to the compressor (21), the outdoor expansion valve (24), and the outdoor fan (28). The controller (40) performs the control in different ways for the cooling operation and the heating operation. That is, components operated in the cooling operation are different from those operated in the heating operation. 15 Therefore, a control block for the cooling operation is shown in FIG. 2, and a control block for the heating operation is shown in FIG. 3. The target low pressure calculator (41) calculates the target low pressure Pis based on a temperature deviation et between a set temperature Ts and the output signal from the indoor temperature sensor (31) (i.e., an indoor temperature Ta). 20 In the cooling operation, the target high pressure calculator (42) calculates the target high pressure Phs based on the output signal from the outdoor temperature sensor (30) (i.e., an outdoor temperature TO), and the output signal from the gas cooler outlet temperature sensor (39) for the cooling operation (i.e., a gas cooler outlet temperature T4). In the heating operation, the target high pressure calculator (42) calculates the target high pressure Phs based 25 on the temperature deviation et, and the output signal from the gas cooler outlet temperature 18 D08WB 148 sensor (37) for the heating operation (i.e., the gas cooler outlet temperature T4). The target discharge temperature calculator (43) calculates the target discharge temperature Tis based on the temperature deviation et, the output signal from the low pressure sensor (32) (i.e., an actual low pressure P1), the output signal from the high pressure 5 sensor (34) (i.e., an actual high pressure Ph), an operation frequency fc of the compressor (21), and the outdoor temperature TO. More specifically, the target discharge temperature calculator (43) calculates the target discharge temperature Tls corresponding to a target degree of superheat based on the temperature deviation et, the actual low pressure Pl, the actual high pressure Ph, the operation frequency fc of the compressor (21), and the outdoor 10 temperature TO. The target low pressure calculator (41), the target high pressure calculator (42), and the target discharge temperature calculator (43) have maps and functions, respectively. Each of the calculators is configured to deliver an output value (a target value) corresponding to the input. 15 Signals input to the control signal generator (49) in the cooling operation are different from those input to the control signal generator (49) in the heating operation. The control signal generator (49) has a plurality of PID control sections (pla, p2a, ..., pib, p2b, ... ) each having a control parameter corresponding to the input signal. In the cooling operation, the control signal generator (49) receives a low pressure 20 deviation el between the target low pressure Pls calculated by the target low pressure calculator (41) and the actual low pressure P1 from the low pressure sensor (32), a high pressure deviation e2 between the target high pressure Phs calculated by the target high pressure calculator (42) and the actual high pressure Ph from the high pressure sensor (34), and a discharge temperature deviation e3 between the target discharge temperature Tls 25 calculated by the target discharge temperature calculator (43) and the output signal from the 19 D08WB148 discharge temperature sensor (33) (i.e., an actual discharge temperature TI). Nine PID control sections (pla, p2a, ...) of the control signal generator (49) are operated in the cooling operation. Specifically, the low pressure deviation el input to the control signal generator (49) is input to the first to third PID control sections (pla, p2a, p3a), 5 the high pressure deviation e2 is input to the fourth to sixth PID control sections (p4a, p5a, p6a), and the discharge temperature deviation e3 are input to the seventh to ninth PID control sections (p7a, p8a, p9a). Each of the first to ninth PID control sections (pla, p2a, ...) delivers an output generated by multiplying the input deviation by a predetermined control parameter. As a 10 result, the control signal generator (49) generates a compressor frequency control signal Afc by adding the output signals from the first, fourth, and seventh PID control sections (p Ia, p4a, p7a), generates an expansion valve control signal Aev by adding the output signals from the second, fifth, and eighth PID control sections (p2a, p5a, p8a), and generates a fan frequency control signal Aff by adding the output signals from the third, sixth, and ninth PID control 15 sections (p3a, p6a, p9a). The compressor frequency control signal Afc, the expansion valve control signal Aev, and the fan frequency control signal Aff generated in this manner are output to the air conditioner (10). In the air conditioner (10), a frequency of AC fed to the motor of the compressor 20 (21) (i.e., the operation frequency) is set to a value corresponding to the compressor frequency control signal Afc, thereby changing the rotation speed of the compressor (21). Thus, the capacity of the compressor (21) varies according to the compressor frequency control signal Afc. A pulse number of the signal fed to the pulse motor of the outdoor expansion valve 25 (24) is set to a value corresponding to the expansion valve control signal Aev. Thus, the 20 D08WBI48 pulse motor of the outdoor expansion valve (24) rotates by an angle corresponding to the pulse number, thereby adjusting the degree of opening of the valve according to the expansion valve control signal Aev. Further, a frequency of AC fed to the motor of the outdoor fan (28) (i.e., the 5 operation frequency) is set to a value corresponding to the fan frequency control signal Aff, thereby changing the rotation speed of the outdoor fan (28). Thus, a flow rate of air fed from the outdoor fan (28) to the outdoor heat exchanger (23) varies according to the fan frequency control signal Aff. The low pressure PI, the discharge temperature TI, and the high pressure Ph of the 10 air conditioner (10) operated in this operation state are fed back to the controller (40) through the low pressure sensor (32), the discharge temperature sensor (33), and the high pressure sensor (34). In this way, the controller (40) performs feed back control to set the low pressure P1 (and an evaporating temperature), the discharge temperature TI (and the degree of superheat), and the high pressure Ph to the target values corresponding to the operation state, 15 respectively. As described above, each of the compressor frequency control signal Afc, the expansion valve control signal Aev, and the fan frequency control signal Aff is generated by associating the low pressure deviation el, the high pressure deviation e2, and the discharge temperature deviation e3 with each other. Specifically, for example, unlike a refrigeration 20 apparatus in which the low pressure of the refrigeration cycle is controlled by the compressor (21), the discharge temperature of the refrigerant is controlled by the outdoor expansion valve (24), and the high pressure of the refrigeration cycle is controlled by the outdoor fan (28), objects of the control corresponding to the physical values, respectively, are not controlled independently. Instead of this, the compressor (21), the outdoor expansion valve (24), and 25 the outdoor fan (28) are concurrently controlled, thereby concurrently, or simultaneously 21 D08WBl48 controlling the high pressure, the low pressure, and the discharge temperature. Specifically, each of the low pressure, the high pressure, and the discharge temperature is not controlled only by one of the compressor (21), the outdoor expansion valve (24), and the outdoor fan (28), but is controlled by all the compressor (21), the outdoor expansion valve (24), and the 5 outdoor fan (28). More specifically, each of the objects of the control, i.e., the compressor (21), the outdoor expansion valve (24), and the outdoor fan (28), is controlled not only based on the changes of the low pressure, the high pressure, and the discharge temperature resulting from the control solely of the each of the objects of control, but is controlled based on the changes of the low pressure, the high pressure, and the discharge temperature resulting from 10 the control of the other objects of control (in other words, the control parameters of the first to nine PID control sections (pla, p2a, ...) are determined so as to take these changes into account). In the heating operation, the control signal generator (49) receives the high pressure deviation e2 between the target high pressure Phs calculated by the target high pressure 15 calculator (42) and the actual high pressure Ph from the high pressure sensor (34), and the discharge temperature deviation e3 between the target discharge temperature TIs calculated by the target discharge temperature calculator (43) and the actual discharge temperature TI of the discharge temperature sensor (33). In the heating operation, four PID control sections (plb, p2b, ...) of the control 20 signal generator (49) are operated. Specifically, the discharge temperature deviation e3 input to the control signal generator (49) is input to the first and second PID control sections (plb, p2b), and the high pressure deviation e2 is input to the third and fourth PID control sections (p3b, p4b). Each of the first to fourth PID control sections (plb, p2b, ...) delivers an output 25 generated by multiplying the input deviation by a predetermined control parameter. As a 22 D08WB 148 result, the control signal generator (49) generates the compressor frequency control signal Afc by adding the output signals from the first and third PID control sections (plb, p3b), and generates the expansion valve control signal Aev by adding the output signals from the second and fourth PID control sections (p2b, p4b). 5 The compressor frequency control signal Afc and the expansion valve control signal Aev generated in this manner are output to the air conditioner (10). In the air conditioner (10), the capacity of the compressor (21) varies according to the compressor frequency control signal Afc, and the degree of opening of the outdoor expansion valve (24) is adjusted according to the expansion valve control signal Aev. 10 The discharge temperature TI and the high pressure Ph of the air conditioner (10) operated in this operation state are fed back to the controller (40) through the discharge temperature sensor (33) and the high pressure sensor (34). In this way, the controller (40) performs feed back control to set the discharge temperature TI (and the degree of superheat), and the high pressure Ph to target values corresponding to the operation state, respectively. 15 As described above, each of the compressor frequency control signal Afc and the expansion valve control signal Aev are generated by associating the high pressure deviation e2 and the discharge temperature deviation e3 with each other. Specifically, for example, unlike a refrigeration apparatus in which the high pressure of the refrigeration cycle is controlled by the compressor (21), and the discharge temperature of the refrigerant is 20 controlled by the outdoor expansion valve (24), the objects of control corresponding to the physical values, respectively, are not controlled independently. Instead of this, the compressor (21) and the outdoor expansion valve (24) are concurrently controlled, thereby concurrently, or simultaneously controlling the high pressure and the discharge temperature. Specifically, each of the high pressure and the discharge temperature is not controlled by only 25 one of the compressor (21) and the outdoor expansion valve (24), but is controlled by both of 23 D08WB148 the compressor (21) and the outdoor expansion valve (24). More specifically, each of the objects of control, i.e., the compressor (21) and the outdoor expansion valve (24), is controlled not only based on the changes of the high pressure and the discharge temperature resulting solely from the control of the each of the objects of control, but is controlled based 5 on the changes of the high pressure and the discharge temperature resulting from the control of the other objects of control (in other words, the control parameters of the first to fourth PID control sections (plb, p2b, ...) are determined so as to take these changes into account). Thus, according to the first embodiment, the plurality of objects of control (e.g., the compressor (21), the outdoor expansion valve (24), etc.) are simultaneously controlled in such 10 a manner that the high pressure of the refrigeration cycle, and the predetermined physical value of the air conditioner (10) are adjusted to the predetermined target values corresponding to the operation state. At the same time, each of the objects of control is controlled in consideration of the changes of the physical value and the high pressure of the refrigeration cycle resulting from the control of the plurality of objects of control. According to these 15 schemes, the capability of the air conditioner (10) (e.g., the low pressure, the degree of superheat, etc., in the cooling operation) can be controlled with the high pressure stably kept to the target value corresponding to the operation state. This can avoid an event in which the control of a target physical value cannot be easily settled, i.e., an event in which adjustment of a first physical value changes a second physical value, and correction of the change of the 20 second physical value by adjusting the second physical value changes a third physical value or the first physical value already adjusted, thereby involving another adjustment. This allows for an improved convergence rate of the control of the capability and the high pressure of the air conditioner (10). According to the present embodiment, three physical values, i.e., the low pressure, 25 the high pressure, and the discharge temperature, are controlled by three objects of control, 24 D08WBI48 i.e., the compressor (21), the outdoor expansion valve (24), and the outdoor fan (28), in the cooling operation. In the heating operation, two physical values, i.e., the high pressure and the discharge temperature, are controlled by two objects of control, i.e., the compressor (21) and the outdoor expansion valve (24). However, some of the objects of control easily have 5 an effect on the physical values, but some do not. That is, even when one of the objects of control is changed, some physical values are less susceptible to the change. In the present embodiment, all the physical values to be controlled are input, and they are associated with each other to generate control signals each corresponding to the objects of control. Instead of this, in generating a control signal for one of the objects of control to which a certain 10 physical value is less susceptible, the degree of association of the certain physical value may be reduced or eliminated (specifically, among the PID control sections (pl a, ... , p1 b, ...) for generating the control signal for the object of control to which a certain physical value is less susceptible, a control parameter of one of the PID control sections corresponding to the certain physical value may be reduced or reduced to zero.) 15 [Second Embodiment] A second embodiment of the present disclosure will be described below. An air conditioner (210) of the second embodiment is different from the air conditioner (10) of the first embodiment in that two expansion valves (24, 26) are provided between an outdoor heat exchanger (23) and an indoor heat exchanger (27) of a refrigerant 20 circuit (220), and that two compressors (21a, 21b) are provided to perform a two-stage compression refrigeration cycle. Specifically, as shown in FIG. 4, the air conditioner (210) includes a refrigerant circuit (220), and a controller (240). The refrigerant circuit (220) connects a low pressure first compressor (21 a), a high 25 pressure second compressor (21b), a four way switching valve (22), an outdoor heat 25 D08WB148 exchanger (23), an outdoor expansion valve (24), a gas-liquid separator (25), an indoor expansion valve (26), and an indoor heat exchanger (27). Specifically, in the refrigerant circuit (220), a discharge side of the second compressor (21b) is connected to a first port of the four way switching valve (22), and a 5 suction side of the first compressor (21a) is connected to a second port of the four way switching valve (22). The first compressor (21a) and the second compressor (21b) are connected through a pipe in such a manner that the refrigerant compressed in and discharged from the first compressor (21a) is sucked into the second compressor (21b) for further compression. In the refrigerant circuit (220), the outdoor heat exchanger (23), the outdoor 10 expansion valve (24), the gas-liquid separator (25), the indoor expansion valve (26), and the indoor heat exchanger (27) are sequentially arranged in a path from a third port to a fourth port of the four way switching valve (22). The gas-liquid separator (25) is connected to the pipe connecting the first compressor (21a) and the second compressor (21b) through a first intermediate pressure refrigerant pipe (25a). 15 The first and second compressors (21a, 21b) are the same as the compressor of the first embodiment. The first and second compressors (21a, 21b) constitute a compression mechanism. Each of the outdoor expansion valve (24) and the indoor expansion valve (26) is comprised of an electronic expansion valve whose degree of opening is variable, and whose 20 valve element (not shown) is driven by a pulse motor (not shown). The outdoor expansion valve (24) constitutes a first expansion mechanism, and the indoor expansion valve (26) constitutes a second expansion mechanism. The gas-liquid separator (25) is a longitudinal, cylindrical hermetic container. The gas-liquid separator (25) is connected to the outdoor expansion valve (24) and the indoor 25 expansion valve (26) through a bridge circuit (50). 26 D08WBI48 Specifically, the outdoor expansion valve (24) is connected to one of terminals of the bridge circuit (50) through a second intermediate pressure refrigerant pipe (25b). The indoor expansion valve (26) is connected to a second terminal of the bridge circuit (50) through a third intermediate pressure refrigerant pipe (25c). An end of a refrigerant inlet 5 pipe (25d) is connected to a third terminal of the bridge circuit (50), and the other end of the refrigerant inlet pipe (25d) is connected to the gas-liquid separator (25). The other end of the refrigerant inlet pipe (25d) penetrates an upper surface of the hermetic container serving as the gas-liquid separator (25), and is positioned in an upper portion of space inside the container. An end of a refrigerant outlet pipe (25e) is connected to a fourth terminal of the 10 bridge circuit (50), and the other end of the refrigerant outlet pipe (25e) is connected to the gas-liquid separator (25). The other end of the refrigerant outlet pipe (25e) penetrates the upper surface of the hermetic container of the gas-liquid separator (25), and is positioned in a lower portion of the space inside the container. An end of the first intermediate pressure refrigerant pipe (25a) close to the gas 15 liquid separator (25) penetrates the upper surface of the hermetic container of the gas-liquid separator (25), and is positioned in the upper portion of the space inside the container. Like the air conditioner of the first embodiment, the air conditioner (210) is able to switchably perform cooling operation and heating operation by switching the four way switching valve (22). 20 In the cooling operation, the four way switching valve (22) is set to the first state. When the first and second compressors (21a, 21b) are driven in this state, the outdoor heat exchanger (23) functions as a radiator (a gas cooler), and the indoor heat exchanger (27) functions as an evaporator to perform the refrigeration cycle. Specifically, an intermediate pressure refrigerant discharged from the first compressor (21a) is compressed in the second 25 compressor (21b) to the supercritical state. The supercritical refrigerant flows into the 27 D08WB148 outdoor heat exchanger (23), and dissipates heat to the outdoor air. After the heat dissipation, the high pressure refrigerant decreases in pressure in the outdoor expansion valve (24) to become a gas-liquid two phase intermediate pressure refrigerant, and flows into the gas-liquid separator (25) through the second intermediate pressure refrigerant pipe (25b), the 5 bridge circuit (50), and the refrigerant inlet pipe (25d). The intermediate pressure refrigerant entered the gas-liquid separator (25) is separated to a liquid refrigerant and a gaseous refrigerant. The intermediate pressure gaseous refrigerant flows from the upper portion in the space inside the gas-liquid separator (25) to the suction side of the second compressor (21b) through the first intermediate pressure refrigerant pipe (25a), merges with the 10 intermediate pressure gaseous refrigerant discharged from the first compressor (21a), and is sucked into the second compressor (21b). The intermediate pressure liquid refrigerant is temporarily stored in the lower portion of the space inside the gas-liquid separator (25), and then exits from the lower portion of the space to pass through the refrigerant outlet pipe (25e), the bridge circuit (50), and the third intermediate pressure refrigerant pipe (25c). Then, the 15 intermediate pressure liquid refrigerant expands (decreases in pressure) in the indoor expansion valve (26) to become a gas-liquid two phase low pressure refrigerant, and flows into the indoor heat exchanger (27). In the indoor heat exchanger (27), the refrigerant absorbs heat from the indoor air to evaporate, and the cooled indoor air is fed to the inside of the room. The evaporated refrigerant is sucked into and compressed in the first compressor 20 (21a). In the heating operation, the four way switching valve (22) is set to the second state. When the first and second compressors (21a, 21b) are operated in this state, the indoor heat exchanger (27) functions as a radiator (a gas cooler), and the outdoor heat exchanger (23) functions as an evaporator to perform the refrigeration cycle. Specifically, an intermediate 25 pressure gaseous refrigerant discharged from the first compressor (21a) is compressed in the 28 D08WB148 second compressor (21b) to the supercritical state. The supercritical refrigerant flows into the indoor heat exchanger (27), and dissipates heat to the indoor air. The heated indoor air is fed to the inside of the room. After the heat dissipation, the refrigerant decreases in pressure in the indoor expansion valve (26) to become a gas-liquid two phase intermediate pressure 5 refrigerant, and flows into the gas-liquid separator (25) through the third intermediate pressure refrigerant pipe (25c), the bridge circuit (50), and the refrigerant inlet pipe (25d). The intermediate pressure refrigerant entered the gas-liquid separator (25) is separated into a liquid refrigerant and a gaseous refrigerant. The intermediate pressure gaseous refrigerant flows from the upper portion of the space inside the gas-liquid separator (25) to the suction 10 side of the second compressor (21b) through the first intermediate pressure refrigerant pipe (25a), merges with the intermediate pressure gaseous refrigerant discharged from the first compressor (21a), and is sucked into the second compressor (21b). The intermediate pressure liquid refrigerant is temporarily stored in the lower portion of the space inside the gas-liquid separator (25), and then flows from the lower portion of the space to the outdoor 15 expansion valve (24) through the refrigerant outlet pipe (25e), the bridge circuit (50), and the second intermediate pressure refrigerant pipe (25b). The intermediate pressure liquid refrigerant expands (decreases in pressure) as it passes through the outdoor expansion valve (24) to become a gas-liquid two phase low pressure refrigerant, and flows into the outdoor heat exchanger (23). In the outdoor heat exchanger (23), the refrigerant absorbs heat from 20 the outdoor air to evaporate. The evaporated refrigerant is sucked into and compressed in the first compressor (21a). The air conditioner (210) configured in this manner includes, in the refrigerant circuit (220), an indoor temperature sensor (31), a low pressure sensor (32), a discharge temperature sensor (33), a high pressure sensor (34), a suction temperature sensor (35), an 25 intermediate pressure saturation temperature sensor (36), a gas cooler outlet temperature 29 D08WB148 sensor (37) for the heating operation. The indoor temperature sensor (31) is a temperature sensing part for sensing the temperature of the indoor air entering the indoor heat exchanger (27). The low pressure sensor (32) is a pressure sensing part for sensing the pressure of the refrigerant sucked into the 5 first compressor (2 1a), i.e., the low pressure of the refrigeration cycle in the refrigerant circuit (220). The discharge temperature sensor (33) is a temperature sensing part for sensing the temperature of the refrigerant discharged from the second compressor (21b). The high pressure sensor (34) is a pressure sensing part for sensing the pressure of the refrigerant discharged from the second compressor (21 b), i.e., the high pressure of the refrigeration cycle 10 in the refrigerant circuit (220). The suction temperature sensor (35) is a temperature sensing part for sensing the temperature of the refrigerant sucked into the first compressor (21a). The intermediate pressure saturation temperature sensor (36) is arranged in the refrigerant outlet pipe (25e) connecting the bridge circuit (50) and the gas-liquid separator (25), and functions as a temperature sensing part for sensing the temperature of the intermediate 15 pressure refrigerant, i.e., the intermediate pressure saturation temperature of the refrigeration cycle. The gas cooler outlet temperature sensor (37) for the heating operation is a temperature sensing part for sensing the temperature of the refrigerant at an outlet of the indoor heat exchanger (27) when the refrigerant circulates in the refrigerant circuit (220) in a heating cycle. 20 The controller (240) is configured to receive output signals from the indoor temperature sensor (31), the low pressure sensor (32), the high pressure sensor (34), the suction temperature sensor (35), the intermediate pressure saturation temperature sensor (36), and the gas cooler outlet temperature sensor (37) for the heating operation, and to control the operation frequencies of the first and second compressors (21a, 21b), and the degrees of 25 opening of the outdoor and indoor expansion valves (24, 26). 30 D08WB148 The controller (240) includes, as shown in FIGS. 5 and 6, a target low pressure calculator (41) for calculating a target low pressure Pls which is a target value of the low pressure of the refrigeration cycle, a target high pressure calculator (42) for calculating a target high pressure Phs which is a target value of the high pressure of the refrigeration cycle, 5 a target superheat degree calculator (44) for calculating the target degree of superheat SHs of the refrigerant which is a target value of the degree of superheat of the refrigerant, an actual superheat degree calculator (45) for calculating the actual degree of superheat SH of the refrigerant, a target intermediate pressure saturation temperature calculator (46) for calculating a target intermediate pressure saturation temperature T3s which is a target value of 10 the intermediate pressure saturation temperature of the refrigerant, a target gas cooler outlet temperature calculator (47) for calculating a target gas cooler outlet temperature T4s which is a target value of the temperature of the refrigerant at an outlet of the gas cooler in the heating operation, and a control signal generator (249) for generating control signals transmitted to the first and second compressors (21 a, 21 b), and the outdoor and indoor expansion valves (24, 15 26). The controller (240) performs the control in different ways for the cooling operation and the heating operation. Therefore, a control block for the cooling operation is shown in FIG. 5, and a control block for the heating operation is shown in FIG. 6. In the cooling operation, the target superheat degree calculator (44) calculates the target degree of superheat SHs of one of the outdoor heat exchanger (23) and the indoor heat 20 exchanger (27) functioning as an evaporator based on a temperature deviation et between a set temperature Ts and an indoor temperature Ta from the indoor temperature sensor (31). In the heating operation, the target superheat degree calculator (44) calculates the target degree of superheat SHs based on the temperature deviation et and an outdoor temperature TO from the outdoor temperature sensor (30). 25 The actual superheat degree calculator (45) calculates the actual degree of superheat 31 D08WBl48 SH of the refrigerant at an outlet of a heat exchanger functioning as an evaporator of the outdoor heat exchanger (23) and the indoor heat exchanger (27) based on an actual low pressure P1 from the low pressure sensor (32) and an actual suction temperature T2 from the suction temperature sensor (35). 5 The target intermediate pressure saturation temperature calculator (46) calculates the target intermediate pressure saturation temperature T3s based on at least one of the outdoor temperature TO from the outdoor temperature sensor (30), the indoor temperature Ta from the indoor temperature sensor (31), an actual high pressure Ph from the high pressure sensor (34), the actual low pressure P1 from the low pressure sensor (32), the target high 10 pressure Phs calculated by the target high pressure calculator (42), and the target low pressure Pls calculated by the target low pressure calculator (41). The target gas cooler outlet temperature calculator (47) calculates the target gas cooler outlet temperature T4s, which is a target value of the temperature of the refrigerant at the outlet of the indoor heat exchanger (27) when the indoor heat exchanger (27) functions as 15 a radiator, based on the temperature deviation et. The target superheat degree calculator (44), the actual superheat degree calculator (45), and the target intermediate pressure saturation temperature calculator (46) have maps and functions, respectively. Each of them is configured to deliver an output value (a target value) corresponding to the input. 20 Signals input to the control signal generator (249) in the cooling operation are different from those input to the control signal generator (249) in the heating operation. The control signal generator (249) has a plurality of PID control sections (pla, p2a, ... , plb, p2b, ... ) each having a control parameter corresponding to the input signal. In the cooling operation, the control signal generator (49) receives a low pressure 25 deviation el between the target low pressure Pls calculated by the target low pressure 32 D08WB148 calculator (41) and the actual low pressure P1 from the low pressure sensor (32), a high pressure deviation e2 between the target high pressure Phs calculated by the target high pressure calculator (42) and the actual high pressure Ph from the high pressure sensor (34), a superheat degree deviation e4 between the target degree of superheat SHs calculated by the 5 target superheat degree calculator (44) and the actual degree of superheat SH calculated by the actual superheat degree calculator (45), and an intermediate pressure saturation temperature deviation e5 between the target intermediate pressure saturation temperature T3s calculated by the target intermediate pressure saturation temperature calculator (46) and the output signal from the intermediate pressure saturation temperature sensor (36) (i.e., an actual 10 intermediate pressure saturation temperature T3). In the cooling operation, sixteen PID control sections (plc, p2c, ...) of the control signal generator (249) are operated. Specifically, the high pressure deviation e2 input to the control signal generator (249) is input to the first to fourth PID control sections (plc-p4c), the intermediate pressure saturation temperature deviation e5 is input to the fifth to eighth PID 15 control sections (p5c-p8c), the low pressure deviation el is input to the ninth to twelfth PID control sections (p9c-pl2c), and the superheat degree deviation e4 is input to the thirteenth to sixteenth PID control sections (pl3c-pl6c). Each of the first to sixteenth PID control sections (plc, p2c, ...) delivers an output generated by multiplying the input deviation by a predetermined control parameter. As a 20 result, the control signal generator (249) generates a first compressor frequency control signal Afcl by adding the output signals from the first, fifth, ninth, and thirteenth PID control sections (ple, p5c, p9c, pl3c), generates a second compressor frequency control signal Afc2 by adding the output signals from the second, sixth, tenth, and fourteenth PID control sections (p2c, p6c, p10c, p14c), generates an outdoor expansion valve control signal Aev1 by adding 25 the output signals from the third, seventh, eleventh, and fifteenth PID control sections (p3c, 33 D08WB148 p7c, p1 Ic, pI5c), and generates an indoor expansion valve control signal Aev2 by adding the output signals from the fourth, eighth, twelfth, and sixteenth PID control sections (p4c, p8c, pl2c, pl6c). The first compressor frequency control signal Afc1, the second compressor 5 frequency control signal Afc2, the outdoor expansion valve control signal Aev1, and the indoor expansion valve control signal Aev2 generated in this manner are output to the air conditioner (210). In the air conditioner (210), the capacity of the first compressor (21a) varies to a value corresponding to the first compressor frequency control signal Afc 1, and the capacity of 10 the second compressor (21b) varies to a value corresponding to the second compressor frequency control signal Afc2. The degree of opening of the outdoor expansion valve (24) is adjusted according to the outdoor expansion valve control signal Aevl, and the degree of opening of the indoor expansion valve (26) is also adjusted according to the indoor expansion valve control signal 15 Aev2. The low pressure P1, the high pressure Ph, the suction temperature T2, and the intermediate pressure saturation temperature T3 in the air conditioner (210) operated in this operation state are fed back to the controller (240) through the low pressure sensor (32), the high pressure sensor (34), the suction temperature sensor (35), and the intermediate pressure 20 saturation temperature sensor (36). Thus, the controller (240) performs feed back control to set the low pressure P1, the high pressure Ph, the degree of superheat SH, and the intermediate pressure saturation temperature T3 to target values corresponding to the operation state, respectively. As described above, each of the first and second compressor frequency control 25 signals Afcl and Afc2, and the outdoor and indoor expansion valve control signals Aevl and 34 D08WB148 Aev2 are generated by associating the low pressure deviation e I, the high pressure deviation e2, the superheat degree deviation e4, and the intermediate pressure saturation temperature deviation e5 with each other. Specifically, the objects of control each corresponding to the physical values are not controlled independently, but the first and second compressors (21a, 5 21b), and the outdoor and indoor expansion valves (24, 26) are controlled concurrently, thereby concurrently, or simultaneously controlling the low pressure, the high pressure, the degree of superheat, and the intermediate pressure saturation temperature. That is, each of the low pressure, the high pressure, the degree of superheat, and the intermediate pressure saturation temperature is not controlled only by one of the first and second compressors (21 a, 10 21b), and the outdoor and indoor expansion valves (24, 26), but is controlled by all the first and second compressors (21a, 21b), and the outdoor and indoor expansion valves (24, 26). More specifically, each of the objects of control, i.e., the first and second compressors (21a, 21b), and the outdoor and indoor expansion valves (24, 26), is controlled not only based on the changes of the low pressure, the high pressure, the degree of superheat, and the 15 intermediate pressure saturation temperature resulting solely from the control of the each of the objects of control, but is controlled based on the changes of the low pressure, the high pressure, the degree of superheat, and the intermediate pressure saturation temperature resulting from the control of the other objects of control (in other words, the control parameters of the first to sixteenth PID control sections (plc, p2c, ...) are determined so as to 20 take these changes into account). In the heating operation, the control signal generator (249) receives the high pressure deviation e2 between the target high pressure Phs calculated by the target high pressure calculator (42) and the actual high pressure Ph from the high pressure sensor (34), the superheat degree deviation e4 between the target degree of superheat SHs calculated by 25 the target superheat degree calculator (44) and the actual degree of superheat SH calculated 35 D08WB148 by the actual superheat degree calculator (45), the intermediate pressure saturation temperature deviation e5 between the target intermediate pressure saturation temperature T3s calculated by the target intermediate pressure saturation temperature calculator (46) and the actual intermediate pressure saturation temperature T3 from the intermediate pressure 5 saturation temperature sensor (36), and the gas cooler outlet temperature deviation e6 between the target gas cooler outlet temperature T4s calculated by the target gas cooler outlet temperature calculator (47) and the output signal from the gas cooler output temperature sensor (37) for the heating operation (i.e., an actual gas cooler outlet temperature T4). In the heating operation, sixteen PID control sections (p Id, p2d, ...) of the control 10 signal generator (249) different from those operated in the cooling operation are operated. Specifically, the high pressure deviation e2 input to the control signal generator (249) is input to the first to the fourth PID control sections (p1 d-p4d), the intermediate pressure saturation temperature deviation e5 is input to the fifth to the eighth PID control sections (p5d-p8d), the gas cooler outlet temperature deviation e6 is input to the ninth to twelfth PID control sections 15 (p9d-pl2d), and the superheat degree deviation e4 is input to the thirteenth to sixteenth PID control sections (p13d-p16d). Each of the first to sixteenth PID control sections (p 1 d, p2d, ...) delivers an output by multiplying the input deviation by a predetermined control parameter. As a result, the control signal generator (249) generates a first compressor frequency control signal Afcl by 20 adding the output signals from the first, fifth, ninth, and thirteenth PID control sections (p Id, p5d, p9d, pl3d), generates a second compressor frequency control signal Afc2 by adding the output signals from the second, sixth, tenth, and fourteenth PID control sections (p2d, p6d, plOd, pl4d), generates an outdoor expansion valve control signal AevI by adding the output signals from the third, seventh, eleventh, and fifteenth PID control sections (p3d, p7d, p1 Id, 25 pl5d), and generates an indoor expansion valve control signal Aev2 by adding the fourth, 36 D08WB 148 eighth, twelfth, and sixteenth PID control sections (p4d, p8d, pl2d, p16d). The first compressor frequency control signal Afcl, the second compressor frequency control signal Afc2, the outdoor expansion valve control signal Aevi, and the indoor expansion valve control signal Aev2 generated in this manner are output to the air 5 conditioner (210). In the air conditioner (210), the capacity of the first compressor (21a) varies according to the first compressor frequency control signal Afcl, the capacity of the second compressor (21b) varies according to the second compressor frequency control signal Afc2. The degree of opening of the outdoor expansion valve (24) is adjusted according to the 10 outdoor expansion valve control signal Aevl, and the degree of opening of the indoor expansion valve (26) is adjusted according to the expansion valve control signal Aev2. The high pressure Ph, the suction temperature T2, the intermediate pressure saturation temperature T3, and the gas cooler outlet temperature T4 in the air conditioner (210) operated in this operation state are fed back to the controller (240) through the high 15 pressure sensor (34), the suction temperature sensor (35), the intermediate pressure saturation temperature sensor (36), and the gas cooler outlet temperature sensor (37) for the heating operation. Thus, the controller (240) performs feed back control to set the high pressure Ph, the degree of superheat SH, the intermediate pressure saturation temperature T3, and the gas cooler outlet temperature T4 to target values corresponding to the operation state, respectively. 20 The first and second compressor frequency control signals Afcl and Afc2, and the outdoor and indoor expansion valve control signals Aevl and Aev2 are generated by associating the high pressure deviation e2, the superheat degree deviation e4, the intermediate pressure saturation temperature deviation e5, and the gas cooler outlet temperature deviation e6 with each other. Specifically, the objects of control each corresponding to the physical 25 values are not controlled independently, but the first and second compressors (2 1a, 21 b), and 37 D08WB148 the outdoor and indoor expansion valves (24, 26) are concurrently controlled, thereby concurrently, or simultaneously controlling the high pressure, the degree of superheat, the intermediate pressure saturation temperature, and the gas cooler outlet temperature. That is, each of the high pressure, the degree of superheat, the intermediate pressure saturation 5 temperature, and the gas cooler outlet temperature is not controlled only by one of the first and second compressors (21 a, 21 b), and the outdoor and indoor expansion valves (24, 26), but is controlled by all the first and second compressors (21a, 21b), and the outdoor and indoor expansion valves (24, 26). More specifically, each of the objects of control, i.e., the first and second compressors (21 a, 21 b), and the outdoor and indoor expansion valves (24, 26), is 10 controlled not only based on the changes of the high pressure, the degree of superheat, the intermediate pressure saturation temperature, and the gas cooler outlet temperature resulting from the control of the each of the objects of control, but is controlled based on the changes of the high pressure, the degree of superheat, the intermediate pressure saturation temperature, and the gas cooler outlet temperature resulting from the control of the other objects of control 15 (in other words, the control parameters of the first to sixteenth PID control sections (plc, p2c, are determined so as to take these changes into account). Thus, according to the second embodiment, the plurality of objects of control (e.g., the first compressor (21a), the outdoor expansion valve (24), etc.) are simultaneously controlled in such a manner that the high pressure of the refrigeration cycle, and the 20 predetermined physical value of the air conditioner (210) are adjusted to the predetermined target values corresponding to the operation state. At the same time, each of the objects of control is controlled in consideration of the changes of the physical value and the high pressure of the refrigeration cycle resulting from the control of the plurality of objects of control. According to these schemes, the capability of the air conditioner (210) (e.g., the low 25 pressure, the degree of superheat, etc., in the cooling operation) can be controlled with the 38 D08WB148 high pressure stably kept to the target value corresponding to the operation state. This can avoid an event in which the control of a target physical value cannot be easily settled, i.e., an event in which adjustment of a first physical value changes a second physical value, and correction of the change of the second physical value by adjusting the second physical value 5 changes a third physical value or the first physical value already adjusted, thereby involving another adjustment. This allows for an improved convergence rate of the control of the capability and the high pressure of the air conditioner (210). According to the present embodiment, four physical values, i.e., the low pressure, the high pressure , the degree of superheat, and the intermediate pressure saturation 10 temperature, are controlled by four objects of control, i.e., the first and second compressors (21a, 21b), and the outdoor and indoor expansion valves (24, 26), in the cooling operation. In the heating operation, four physical values, i.e., the high pressure, the degree of superheat, the intermediate pressure saturation temperature, and the gas cooler outlet temperature, are controlled by four objects of control, i.e., the first and second compressors (21a, 21b), and the 15 outdoor and indoor expansion valves (24, 26). However, some of the objects of control easily have an effect on the physical values, but some do not. That is, even when one of the objects of control is changed, some physical values are less susceptible to the change. In the present embodiment, all the physical values to be controlled are input, and they are associated with each other to generate control signals each corresponding to the objects of control. In 20 generating a control signal for one of the objects of control to which a certain physical value is less susceptible, the degree of association of the certain physical value may be reduced or eliminated (specifically, among the PID control sections (plc, ... , pld, ... ) for generating the control signal for the object of control to which a certain physical value is less susceptible, a control parameter of one of the PID control sections corresponding to the certain physical 25 value may be reduced or reduced to zero.) 39 D08WB148 [Third Embodiment] A third embodiment of the present disclosure will be described below. An air conditioner (310) of the third embodiment is different from the air conditioner (10) of the first embodiment in that a plurality of indoor heat exchangers (27a, 5 27b) are provided in a refrigerant circuit (320). Specifically, the air conditioner (310) includes a refrigerant circuit (320), and a controller (340) as shown in FIG. 7. The refrigerant circuit (320) connects a compressor (21), a four way switching valve (22), an outdoor heat exchanger (23), an outdoor expansion valve (24), a receiver (25), a first 10 and second indoor expansion valves (26a, 26b), and first and second indoor heat exchangers (27a, 27b). In this refrigerant circuit (320), a plurality of (two in the present embodiment) indoor heat exchangers (27a, 27b) are connected in parallel, and an indoor expansion valve (26a (26b)) is connected to each of the indoor heat exchangers (27a (27b)). Specifically, in the refrigerant circuit (320), a discharge side of the compressor (21) 15 is connected to a first port of the four way switching valve (22), and a suction side of the compressor (21) is connected to a second port of the four way switching valve (22). In the refrigerant circuit (320), the outdoor heat exchanger (23), the outdoor expansion valve (24), the receiver (25), the two indoor expansion valves (26a, 26b), and the two indoor heat exchangers (27a, 27b) are sequentially arranged in a path from a third port to a fourth port of 20 the four way switching valve (22). Each of the outdoor expansion valve (24), and the first and second indoor heat expansion valves (26a, 26b) is comprised of an electronic expansion valve whose degree of opening is variable, and whose valve element (not shown) is driven by a pulse motor (not shown). The outdoor expansion valve (24) constitutes a heat source side expansion 25 mechanism, and the first and second indoor expansion valves (26a, 26b) constitute a 40 D08WB148 utilization side expansion mechanism. The first and second indoor heat exchangers (27a, 27b) are provided with first and second indoor fans (29a, 29b), respectively. Like the air conditioner of the first embodiment, the air conditioner (310) is able to 5 switchably perform cooling operation and heating operation by switching the four way switching valve (22). In the cooling operation, the four way switching valve (22) is set to the first state. When the compressor (21) is operated in this state, the outdoor heat exchanger (23) functions as a radiator, and the first and second indoor heat exchangers (27a, 27b) function as 10 evaporators to perform the refrigeration cycle. Specifically, the refrigerant in the supercritical state discharged from the compressor (21) flows into the outdoor heat exchanger (23), and dissipates heat to the outdoor air. After the heat dissipation, the refrigerant expands (decreases in pressure) as it passes through the outdoor expansion valve (24). The expanded refrigerant passes through the receiver (25), and is branched, and the branched 15 flows of the refrigerant pass through the first and second indoor expansion valves (26a, 26b). At this time, the refrigerant further expands (decreases in pressure), and flows into the first and second indoor heat exchangers (27a, 27b). That is, the refrigerant flowing between the outdoor expansion valve (24) and the indoor expansion valves (26a, 26b), and in the receiver (25) is at an intermediate pressure. In the first and second indoor heat exchangers (27a, 27b), 20 the refrigerant absorbs heat from the indoor air to evaporate, and the cooled air is fed to the inside of the room. The evaporated refrigerant is sucked into and compressed in the compressor (21). In the heating operation, the four way switching valve (22) is set to the second state. When the compressor (21) is operated in this state, the first and second indoor heat 25 exchangers (27a, 27b) function as radiators, and the outdoor heat exchanger (23) functions as 41 D08WB148 an evaporator to perform the refrigeration cycle. Specifically, the refrigerant discharged from the compressor (21) in the supercritical state is branched, and the branched flows of the refrigerant enter the first and second indoor heat exchangers (27a, 27b), respectively, and dissipate heat to the indoor air. The heated indoor air is fed to the inside of the room. After 5 the heat dissipation, the refrigerant expands (decreases in pressure) as it passes through the second indoor expansion valves (26a, 26b). The expanded refrigerant passes through the receiver (25), and then further expands (decreases in pressure) as it passes through the outdoor expansion valve (24). That is, the refrigerant flowing between the first and second indoor expansion valves (26a, 26b) and the outdoor expansion valve (24), and in the receiver (25) is 10 at the intermediate pressure. The refrigerant expanded by the outdoor expansion valve (24) flows into the outdoor heat exchanger (23), and absorbs heat from the outdoor air to evaporate. The evaporated refrigerant is sucked into and compressed in the compressor (21). The air conditioner (310) configured in this manner includes, in the refrigerant circuit (320), first and second indoor temperature sensors (31 a, 31 b), a low pressure sensor 15 (32), a high pressure sensor (34), a suction temperature sensor (35), first and second gas cooler outlet temperature sensors (37a, 37b) for the heating operation, first and second evaporator outlet temperature sensors (38a, 38b), and a gas cooler outlet temperature sensor (39) for the cooling operation. The first and second indoor temperature sensors (31 a, 31 b) are sensing parts for 20 sensing the temperatures of the flows of the indoor air entering the first and second indoor heat exchangers (27a, 27b), and are provided for the first and second indoor heat exchangers (27a, 27b), respectively. The first and second gas cooler outlet temperature sensors (37a, 37b) for the heating operation are temperature sensing parts for sensing the temperatures of the refrigerant at the outlets of the first and second indoor heat exchangers (27a, 27b), 25 respectively, when the refrigerant circulates in the refrigerant circuit (320) in the heating cycle. 42 D08WB1 48 The first and second gas cooler outlet temperature sensors (37a, 37b) for the heating operation are provided for the first and second indoor heat exchangers (27a, 27b), respectively. The first and second evaporator outlet temperature sensors (38a, 38b) are temperature sensing parts for sensing the temperatures of the refrigerant at the outlets of the first and second 5 indoor heat exchangers (27a, 27b), respectively, when the refrigerant circulates in the refrigerant circuit (320) in the cooling cycle, and are provided for the first and second indoor heat exchangers (27a, 27b), respectively. The controller (340) is configured to receive output signals from the first and second indoor temperature sensors (3 la, 3 lb), the low pressure sensor (32), the high pressure 10 sensor (34), the suction temperature sensor (35), the first and second gas cooler outlet temperature sensors (37a, 37b) for the heating operation, and the first and second evaporator outlet temperature sensors (38a, 38b), and to control the operation frequency of the compressor (21), and the degrees of opening of the outdoor, first, and second indoor expansion valves (24, 26a, 26b). 15 The controller (340) includes, as shown in FIGS. 8 and 9, a target low pressure calculator (41) for calculating a target low pressure Pls which is a target value of the low pressure of the refrigeration cycle, a target high pressure calculator (42) for calculating a target high pressure Phs which is a target value of the high pressure of the refrigeration cycle, an actual superheat degree calculator (45) for calculating the actual degree of superheat SH 20 which is the actual degree of superheat of the refrigerant, a target first superheat degree calculator (44a) for calculating a target first degree of superheat SHas which is a target value of the degree of superheat of the refrigerant at the outlet of the first indoor heat exchanger (27a) in the cooling operation, a target second superheat degree calculator (44b) for calculating a target second degree of superheat SHbs which is a target value of the degree of 25 superheat of the refrigerant at the outlet of the second indoor heat exchanger (27b) in the 43 D08WB148 cooling operation, a target first gas cooler outlet temperature calculator (47a) for calculating a target first gas cooler outlet temperature T4as which is a target value of the temperature of the refrigerant at the outlet of the first indoor heat exchanger (27a) in the heating operation, a target second gas cooler outlet temperature (47b) for calculating a target second gas cooler 5 outlet temperature T4bs which is a target value of the temperature of the refrigerant at the outlet of the second indoor heat exchanger (27b) in the heating operation, a target superheat degree calculator (44) for calculating the target degree of superheat SHs which is a target value of the degree of superheat of the refrigerant at the outlet of the outdoor heat exchanger (23) in the heating operation, and a control signal generator (349) for generating control 10 signals transmitted to the compressor (21), and the outdoor, first, and second indoor expansion valves (24, 26a, 26b). The controller (340) performs the control in different ways for the cooling operation and the heating operation. Therefore, a control block for the cooling operation is shown in FIG. 8, and a control block for the heating operation is shown in FIG. 9. 15 The target low pressure calculator (41) calculates the target low pressure Pls of the air conditioner (310) as a whole based on a temperature deviation eta between a set temperature Tsa of the first indoor heat exchanger (27a) and an indoor temperature Taa from the first indoor temperature sensor (31 a), and a temperature deviation etb between a set temperature Tsb of the second indoor heat exchanger (27b) and an indoor temperature Tab 20 from the second indoor temperature sensor (31 b). In the cooling operation, the target high pressure calculator (42) calculates the target high pressure Phs of the air conditioner (310) based on an outdoor temperature TO from the outdoor temperature sensor (30), and a gas cooler outlet temperature T4 from the gas cooler outlet temperature sensor (39) for the cooling operation. In the heating operation, the target 25 high pressure calculator (42) calculates the target high pressure Phs of the air conditioner 44 D08WB 148 (310) based on at least one of the temperature deviation eta of the first indoor heat exchanger (27a), the temperature deviation etb of the second indoor heat exchanger (27b), the target first gas cooler outlet temperature T4as calculated by the target first gas cooler outlet temperature calculator (47a), the target second gas cooler outlet temperature T4bs calculated by the target 5 second gas cooler outlet temperature calculator (47b), and the first and second gas cooler outlet temperatures T4a, T4b from the first and second gas cooler outlet temperature sensors (37a, 37b) for the heating operation. The target first superheat degree calculator (44a) calculates the target first degree of superheat SHas based on the temperature deviation eta of the first indoor heat exchanger (27a). 10 The target second superheat degree calculator (44b) calculates the target second degree of superheat SHbs based on the temperature deviation etb of the second indoor heat exchanger (27b). In the cooling operation, the actual superheat degree calculator (45) calculates an actual first or actual second degree of superheat SHa or SHb, which is the actual degree of 15 superheat of the refrigerant at the outlet of the first or second indoor heat exchanger (27a, 27b), based on the actual low pressure P1 from the low pressure sensor (32), and the first or second evaporator outlet temperature T5a or Tbb from the first or second evaporator outlet temperature sensor (38a, 38b). In the heating operation, the actual superheat degree calculator (45) calculates the actual degree of superheat SH, which is the actual degree of 20 superheat of the refrigerant at the outlet of the outdoor heat exchanger (23), based on the actual low pressure P1 from the low pressure sensor (32), and the actual suction temperature T2 from the suction temperature sensor (35). The target first gas cooler outlet temperature calculator (47a) calculates the target first gas cooler outlet temperature T4as based on the temperature deviation eta of the first 25 indoor heat exchanger (27a). 45 D08WBI48 The target second gas cooler outlet temperature calculator (47b) calculates the target second gas cooler outlet temperature T4bs based on the temperature deviation etb of the second indoor heat exchanger (27b). The target low pressure calculator (41), the target high pressure calculator (42), the 5 target first superheat degree calculator (44a), the target second superheat degree calculator (44b), the target superheat degree calculator (44), the target first gas cooler outlet temperature calculator (47a), and the target second gas cooler outlet temperature calculator (47b) have maps and functions, respectively. Each of them is configured to output an output value corresponding to the input. 10 Signals input to the control signal generator (349) in the cooling operation are different from those input to the control signal generator (349) in the heating operation. The control signal generator (349) has PID control sections (ple, p2e, ... , plf, p2f, ... ) each having a control parameter corresponding to the input signal. In the cooling operation, the control signal generator (349) receives a low pressure 15 deviation el between the target low pressure Pls calculated by the target low pressure calculator (41) and the actual low pressure P1 from the low pressure sensor (32), a high pressure deviation e2 between the target high pressure Phs calculated by the target high pressure calculator (42) and the actual high pressure Ph from the high pressure sensor (34), a first superheat degree deviation e4a between the target degree of superheat SHas calculated by 20 the target first superheat degree calculator (44a) and the actual first degree of superheat SHa of the first indoor heat exchanger (27a) calculated by the actual superheat degree calculator (45), and the second superheat degree deviation e4b between the target degree of superheat SHbs calculated by the target second superheat degree calculator (44b) and the actual second degree of superheat SHb of the second indoor heat exchanger (27b) calculated by the actual 25 superheat degree calculator (45). 46 D08WB! 48 In the cooling operation, sixteen PID control sections (ple, p2e, ...) of the control signal generator (349) are operated. Specifically, the low pressure deviation el input to the control signal generator (349) is input to the first to fourth PID control sections (ple-p4e), the high pressure deviation e2 is input to the fifth to eighth PID control sections (p5e-p8e), the 5 first superheat degree deviation e4a is input to the ninth to twelfth PID control sections (p9e pl2e), and the second superheat degree deviation e4b is input to the thirteenth to sixteenth PID control sections (p1 3e-p16e). Each of the first to sixteenth PID control sections (ple, p2e, ...) delivers an output generated by multiplying the input deviation by a predetermined control parameter. 10 Specifically, the control signal generator (349) generates a compressor frequency control signal Afc by adding output signals from the first, fifth, ninth, and thirteenth PID control sections (ple, p5e, p9e, pl3e), generates an outdoor expansion valve control signal Aevi by adding output signals from the second, sixth, tenth, and fourteenth PID control sections (p2e, p6e, p10e, pl4e), generates a first indoor expansion valve control signal Aev2a by adding 15 output signals from the third, seventh, eleventh, and fifteenth PID control sections (p3e, p7e, pl e, pI5e), and generates a second indoor expansion valve control signal Aev2b by adding output signals from the fourth, eighth, twelfth, and sixteenth PID control sections (p4e, p8e, pl2e, pl6e). The compressor frequency control signal Afc, the outdoor expansion valve control 20 signal Aevl, the first indoor expansion valve control signal Aev2a, and the second indoor expansion valve control signal Aev2b are output to the air conditioner (310). In the air conditioner (310), the capacity of the compressor (21) varies to a value corresponding to the compressor frequency control signal Afc. The degree of opening of the outdoor expansion valve (24) is adjusted according to 25 the outdoor expansion valve control signal Aevl, and the degree of opening of the first indoor 47 D08WB148 expansion valve (26a) is adjusted according to the first indoor expansion valve control signal Aev2a, and the degree of opening of the second indoor expansion valve (26b) is adjusted according to the second indoor expansion valve control signal Aev2b. The low pressure P1, the high pressure Ph, the first evaporator outlet temperature 5 T5a of the first indoor heat exchanger (27a), and the second evaporator outlet temperature T5b of the second indoor heat exchanger (27b) of the air conditioner (310) operated in this operation state are fed back to the controller (340) through the low pressure sensor (32), the high pressure sensor (34), and the first and second evaporator outlet temperature sensors (38a, 38b). Thus, the controller (340) performs feed back control to set the low pressure PI, the 10 high pressure Ph, and the first and second degrees of superheat SHa and SHb to target values corresponding to the operation state, respectively. As described above, each of the compressor frequency control signal Afc, and the outdoor, first indoor, and second indoor expansion valve control signals AevI, Aev2a, and Aev2b is generated by associating the low pressure deviation el, the high pressure deviation 15 e2, the first superheat degree deviation e4a, and the second superheat degree deviation e4b with each other. Specifically, the objects of control each corresponding to the physical values are not controlled independently, but the compressor (21), the outdoor expansion valve (24), and the first and second indoor expansion valves (26a, 26b) are controlled concurrently, thereby concurrently, or simultaneously controlling the low pressure, the high pressure, the 20 first degree of superheat, and the second degree of superheat. That is, each of the low pressure, the high pressure, the first degree of superheat, and the second degree of superheat is not controlled only by one of the compressor (21), the outdoor expansion valve (24), and the first and second indoor expansion valves (26a, 26b), but is controlled by all the compressor (21), the outdoor expansion valve (24), and the first and second indoor expansion valves (26a, 25 26b). More specifically, each of the objects of control, i.e., the compressor (21), the outdoor 48 D08WB148 expansion valve (24), and the first and second indoor expansion valves (26a, 26b), is not controlled not only based on the changes of the low pressure, the high pressure, the first degree of superheat, and the second degree of superheat resulting from the control of the each of the objects of control, but is controlled based on the changes of the low pressure, the high 5 pressure, the first degree of superheat, and the second degree of superheat resulting from the control of the other objects of control (in other words, the control parameters of the first to sixteenth PID control sections (ple, p2e, ...) are determined so as to take these changes into account). In the heating operation, the control signal generator (349) receives a high pressure 10 deviation e2 between the target high pressure Phs calculated by the target high pressure calculator (42) and the actual high pressure Ph from the high pressure sensor (34), a superheat degree deviation e4 between the target degree of superheat SHs calculated by the target superheat degree calculator (44) and the actual degree of superheat SH calculated by the actual superheat degree calculator (45), a first gas cooler outlet temperature deviation e6a 15 between the target first gas cooler outlet temperature T4as calculated by the target first gas cooler outlet temperature calculator (47a) and the actual first gas cooler outlet temperature T4a from the first gas cooler outlet temperature sensor (37a) for the heating operation, and a second gas cooler outlet temperature deviation e6b between the target second gas cooler outlet temperature T4bs calculated by the target second gas cooler outlet temperature 20 calculator (47b) and the actual second gas cooler outlet temperature T4b from the second gas cooler outlet temperature sensor (37b) for the heating operation. In the heating operation, sixteen PID control sections (plf, p2f, ...) of the control signal generator (349) different from those operated in the cooling operation are operated. Specifically, the high pressure deviation e2 input to the control signal generator (349) is input 25 to the first to fourth PID control sections (plf-p4f), the first gas cooler outlet temperature 49 D08WB 148 deviation e6a is input to the fifth to the eighth PID control sections (p5f- p8f), the second gas cooler outlet temperature deviation e6b is input to the ninth to the twelfth PID control sections (p9f-pl2f), and the superheat degree deviation e4 is input to the thirteenth to sixteenth PID control sections (pl3f-pl6f). 5 Each of the first to sixteenth PID control sections (plf, p2f, ...) delivers an output generated by multiplying the input deviation by a predetermined control parameter. Specifically, the control signal generator (349) generates a compressor frequency control signal Afc by adding output signals from the first, fifth, ninth, and thirteenth PID control sections (plf, p5f, p9f, pl3f), generates an outdoor expansion valve control signal Aevi by 10 adding output signals from the second, sixth, tenth, and fourteenth PID control sections (p2f, p6f, pl0f, pl4f), generates a first indoor expansion valve control signal Aev2a by adding output signals from the third, seventh, eleventh, and fifteenth PID control sections (p3f, p7f, p IIf, p1 5f), and generates a second indoor expansion valve control signal Aev2b by adding output signals from the fourth, eighth, twelfth, and sixteenth PID control sections (p4f, p8f, 15 pl2f, pl6f). The compressor frequency control signal Afc, the outdoor expansion valve control signal Aevl, the first indoor expansion valve control signal Aev2a, and the second indoor expansion valve control signal Aev2b generated in this manner are output to the air conditioner (310). 20 In the air conditioner (310), the capacity of the compressor (21) varies to a value corresponding to the compressor frequency control signal Afc. The degree of opening of the outdoor expansion valve (24) is adjusted according to the outdoor expansion valve control signal Aev1, the degree of the first indoor expansion valve (26a) is adjusted according to the first indoor expansion valve control signal Aev2a, and 25 the degree of opening of the second indoor expansion valve (26b) is adjusted according to the 50 D08WB1 48 second indoor expansion valve control signal Aev2b. The low pressure P1, the high pressure Ph, the first gas cooler outlet temperature T4a of the first indoor heat exchanger (27a), and the second gas cooler outlet temperature T4b of the second indoor heat exchanger (27b) in the air conditioner (310) operated in this 5 operation state are fed back to the controller (340) through the low pressure sensor (32), the high pressure sensor (34), and the first and second gas cooler outlet temperature sensors (37a, 37b) for the heating operation. Thus, the controller (340) performs feed back control to set the low pressure P1, the high pressure Ph, and the first and second degrees of superheat SHa and SHb to target values corresponding to the operation state, respectively. 10 Each of the compressor frequency control signal Afc, the outdoor expansion valve control signal Aevl, and the first and second indoor expansion valve control signals Aev2a and Aev2b is generated by associating the high pressure deviation e2, the superheat degree deviation e4, the first gas cooler outlet temperature deviation e6a, and the second gas cooler outlet temperature deviation e6b with each other. Specifically, the objects of control each 15 corresponding to the physical values are not controlled independently, but the compressor (21), the outdoor expansion valve (24), and the first and second indoor expansion valves (26a, 26b), are controlled concurrently, thereby concurrently, or simultaneously controlling the high pressure, the degree of superheat, the first gas cooler outlet temperature, and the second gas cooler outlet temperature. That is, each of the high pressure, the degree of superheat, the 20 first gas cooler outlet temperature, and the second gas cooler outlet temperature is not controlled only by one of the compressor (21), the outdoor expansion valve (24), and the first and second indoor expansion valves (26a, 26b), but is controlled by all the compressor (21), the outdoor expansion valve (24), and the first and second indoor expansion valves (26a, 26b). More specifically, the objects of control, i.e., the compressor (21), the outdoor expansion 25 valve (24), and the first and second indoor expansion valves (26a, 26b) is controlled not only 51 D08WB148 based on the changes of the high pressure, the degree of superheat, the first gas cooler outlet temperature, and the second gas cooler outlet temperature resulting from the control of the each of the objects of control, but is controlled based on the changes of the high pressure, the degree of superheat, the first and second gas cooler outlet temperatures resulting from the 5 control of the other objects of control (in other words, the control parameters of the first to sixteenth PID control sections (plf, p2f, ...) are determined so as to take these changes into account). Thus, according to the third embodiment, the plurality of objects of control (e.g., the compressor (21), the outdoor expansion valve (24), etc.) are simultaneously controlled in such 10 a manner that the high pressure of the refrigeration cycle, and the predetermined physical value of the air conditioner (310) are adjusted to the predetermined target values corresponding to the operation state. At the same time, each of the objects of control is controlled in consideration of the changes of the physical value and the high pressure of the refrigeration cycle resulting from the control of the plurality of objects of control. 15 According to these schemes, the capability of the air conditioner (310) (e.g., the low pressure, the degree of superheat, etc. in the cooling operation) can be controlled with the high pressure stably kept to the target value corresponding to the operation state. This can avoid an event in which the control of a target physical value cannot be easily settled, i.e., an event in which adjustment of a first physical value changes a second physical value, and correction of the 20 change of the second physical value by adjusting the second physical value changes a third physical value or the first physical value already adjusted, thereby involving another adjustment. This allows for improved settling of the control of the capability and the high pressure of the air conditioner (310). In the present embodiment, four physical values, i.e., the low pressure, the high 25 pressure, the first degree of superheat, and the second degree of superheat, are controlled by 52 D08WB148 the four objects of control, i.e., the compressor (21), the outdoor expansion valve (24), and the first and second indoor expansion valves (26a, 26b), in the cooling operation. In the heating operation, four physical values, i.e., the high pressure, the first gas cooler outlet temperature, the second gas cooler outlet temperature, and the degree of superheat, are controlled by four 5 objects of control, i.e., the compressor (21), the outdoor expansion valve (24), and the first and second indoor expansion valves (26a, 26b). However, some of the objects of control easily have an effect on the physical values, but some do not. That is, even when one of the objects of control is changed, some physical values are less susceptible to the change. In the present embodiment, all the physical values to be controlled are input, and they are associated 10 with each other to generate control signals each corresponding to the objects of control. In generating a control signal for one of the objects of control to which a certain physical value is less susceptible, the degree of association of the certain physical value may be reduced or eliminated (specifically, among the PID control sections (ple, ... , plf, ... ) for generating the control signal for the object of control to which a certain physical value is less susceptible, a 15 control parameter of one of the PID control sections corresponding to the certain physical value may be reduced or reduced to zero.) [Other Embodiments] The above-described embodiments may be modified in the following manner. Specifically, the present disclosure is not limited to the refrigerant circuit described 20 in the above embodiments, but is applicable to any refrigerant circuits. For example, as shown in FIG. 10, the disclosed technique may be applied to a multi-type air conditioner (410) which performs a two-stage compression refrigeration cycle, and includes a plurality of indoor units. In this case, for example, the high pressure, the low pressure, the first evaporator outlet temperature, the second evaporator outlet temperature, and the intermediate 25 pressure saturation temperature may be input, and these physical values may be associated to 53 D08WB148 generate control signals for controlling the first and second compressors (21 a, 21 b), the first and second indoor expansion valves (26a, 26b), and the outdoor expansion valve (24), respectively. As a result, the control signals for the first and second compressors (21a, 21b), the first and second indoor expansion valves (26a, 26b), and the outdoor expansion valve (24) 5 are generated, i.e., the first and second compressors (21 a, 21 b), the first and second indoor expansion valves (26a, 26b), and the outdoor expansion valve (24) are controlled, in such a manner that the high pressure, the low pressure, the first evaporator outlet temperature, the second evaporator outlet temperature, and the intermediate pressure saturation temperature are set to predetermined target values, respectively, when adjustment of all the first and second 10 compressors (21a, 21b), the first and second indoor expansion valves (26a, 26b), and the outdoor expansion valve (24) is done. For example, as shown in FIG. 11, the disclosed technique may be applied to a multi-type air conditioner (510) which performs a two-stage compression refrigeration cycle, and includes an internal heat exchanger (51) between the outdoor heat exchanger (23) and the 15 outdoor expansion valve (24), and a plurality of indoor units. Specifically, the air conditioner (510) includes a bypass pipe (53) branched from a connection pipe (52) connecting the outdoor heat exchanger (23) and the receiver (25), and is connected to a pipe connecting the first compressor (21 a) and the second compressor (21 b). A bypass expansion valve (54) is provided in the bypass pipe (53). The refrigerant flowing 20 in the bypass pipe (53) decreases in pressure as it passes through the bypass expansion valve (54), and becomes an intermediate pressure refrigerant. Further, an outdoor expansion valve (24) is provided in the connection pipe (52) to be positioned closer to the receiver (25) than to the junction with the bypass pipe (53). The internal heat exchanger (51) is provided on the connection pipe (52) between 25 the junction with the bypass pipe (53) and the outdoor expansion valve (24), and on the 54 D08WB148 bypass pipe (53) downstream of the bypass expansion valve (54), thereby performing heat exchange between the refrigerants flowing the pipes, respectively. Specifically, in the cooling operation, the refrigerant flowing in the bypass pipe (53) decreases in pressure as it passes through the bypass expansion valve (54) to become an intermediate pressure liquid or 5 an intermediate pressure gas-liquid two-phase refrigerant. Then, the refrigerant passes through the internal heat exchanger (51), absorbs heat from the refrigerant flowing in the connection pipe (52) to become a superheated gaseous refrigerant, and flows into the suction side of the second compressor (21b). The refrigerant flowing in the connection pipe (52) exits from the outdoor heat exchanger (23), flows into the internal heat exchanger (51), and 10 dissipates heat to the refrigerant flowing in the bypass pipe (53) to become a supercooled refrigerant. Then, the refrigerant decreases in pressure in the outdoor expansion valve (24) to become an intermediate pressure refrigerant, and flows into the receiver (25). A receiver pressure saturation temperature sensor (55) is arranged at the connection pipe (52) closer to the receiver (25) than to the outdoor expansion valve (24). An 15 intermediate pressure saturation temperature sensor (36) is arranged at the bypass pipe (53) downstream of the internal heat exchanger (51). In the air conditioner (510) configured in this manner, for example, the high pressure, the low pressure, the first evaporator outlet temperature, the second evaporator outlet temperature, the intermediate pressure saturation temperature, and an internal pressure 20 of the receiver sensed by the receiver pressure saturation temperature sensor (55) are input, and these physical values are associated with each other to generate control signals for controlling the first and second compressors (21a, 21b), the first and second indoor expansion valves (26a, 26b), the outdoor expansion valve (24), and the bypass expansion valve (54), respectively. As a result, the control signals for the first and second compressors (21 a, 21 b), 25 the first and second indoor expansion valves (26a, 26b), the outdoor expansion valve (24), 55 D08WB148 and the bypass expansion valve (54), respectively, are generated, i.e., the first and second compressors (21a, 21b), the first and second indoor expansion valves (26a, 26b), the outdoor expansion valve (24), and the bypass expansion valve (54) are controlled in such a manner that the high pressure, the low pressure, the first evaporator outlet temperature, the second 5 evaporator outlet temperature, the intermediate pressure saturation temperature, and the internal pressure of the receiver are set to the predetermined target values, respectively, when adjustment of all the first and second compressors (21a, 21b), the first and second indoor expansion valves (26a, 26b), the outdoor expansion valve (24), and the bypass expansion valve (54) is done. 10 Further, in the second embodiment, two compressors (21 a, 21 b), and two expansion valves (24, 26) are provided to perform a two-stage compression refrigeration cycle. However, a single compressor may be provided, and gas injection may be performed during the compression in the compressor. In this case, the number of objects of control is three including the single compressor and the two expansion valves (24, 26). Therefore, the 15 number of physical values to be controlled is preferably three in total (including at least the high pressure of the refrigeration cycle.) In the above embodiments, a plurality of physical values is input, and outputs generated by multiplying the input physical values by control parameters, respectively, are added to generate a control signal for one object of control. However, the disclosed 20 technique is not limited to this configuration. For example, a plurality of physical values may be input, and they may be multiplied by a matrix constituted of the control parameters, to calculate a plurality of control signals as outputs based on a dynamic model of the refrigeration cycle in each of the refrigerant circuits. Even in this configuration, the input physical values are associated with each other to generate the control signal for the objects of 25 control. Thus, concurrent control of the plurality of objects of control allows for concurrent 56 D08WB148 control of the plurality of physical values, thereby allowing for an improved convergence rate of the control of each of the physical values. In the above embodiments, the expansion valve is employed as the expansion mechanism. However, the disclosed technique is not limited thereto, and an expansion unit 5 may be used. In the first embodiment only, the outdoor fan (28) is controlled as the object of control. However, in the other embodiments, the outdoor fan (28) may be used in combination to perform control of the high pressure and the capability of the apparatus. The above embodiments are merely preferred embodiments in nature, and are not 10 intended to limit the scope, applications and use of the disclosed technique. INDUSTRIAL APPLICABILITY As described above, the present disclosure is useful for a refrigeration apparatus including a refrigerant circuit for performing a supercritical refrigeration cycle. DESCRIPTION OF REFERENCE CHARACTERS 15 20 Refrigerant circuit 21 Compressor (compression mechanism) 21a First compressor (compressor mechanism) 21b Second compressor (compressor mechanism) 23 Outdoor heat exchanger (heat source side heat exchanger) 20 24 Outdoor expansion valve (expansion mechanism, first expansion mechanism, heat source side expansion mechanism) 26 Indoor expansion valve (expansion mechanism, second expansion mechanism) 26a First indoor expansion valve (utilization side expansion mechanism) 26b Second indoor expansion valve (utilization side expansion mechanism) 25 27 Indoor heat exchanger (utilization side heat exchanger) 57 D08WB1 48 27a First indoor heat exchanger (utilization side heat exchanger) 27b Second indoor heat exchanger (utilization side heat exchanger) 28 Outdoor fan (heat source side fan) 40, 240, 340 Controller (control section) 58 D08WB148

Claims

1. A refrigeration apparatus comprising: a refrigerant circuit (20) sequentially connecting a compression mechanism (21), a 5 heat source side heat exchanger (23), an expansion mechanism (24), and a utilization side heat exchanger (27), and performing a supercritical refrigeration cycle in which a high pressure is a supercritical pressure of a refrigerant or higher; and a control section (40) for controlling a plurality of objects of control including at least the compression mechanism (21) and the expansion mechanism (24), wherein 10 the control section (40) concurrently controls the plurality of objects of control, thereby concurrently controlling a predetermined physical value as an index of a capability of the refrigeration apparatus, and the high pressure of the refrigeration cycle.

2. The refrigeration apparatus of claim 1, wherein 15 the control section (40) receives the predetermined physical value, and the high pressure of the refrigeration cycle as inputs, generates control signals each corresponding to the plurality of objects of control by associating the physical value and the high pressure with each other, and outputs the control signals to the corresponding objects of control, respectively, thereby concurrently controlling the predetermined physical value, and the high 20 pressure of the refrigeration cycle.

3. The refrigeration apparatus of claim 1, further comprising: a heat source side fan (28) for feeding air to the heat source side heat exchanger (23) in which the refrigerant exchanges heat with the air, wherein 25 in cooling operation, 59 D08WB1 48 the predetermined physical value includes, an evaporating temperature of the refrigerant in the utilization side heat exchanger (27), and a degree of superheat of the refrigerant at an outlet of the utilization side heat exchanger (27), the objects of control further include the heat source side fan (28), and 5 the control section (40) receives the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, and the high pressure of the refrigeration cycle as inputs, and concurrently controls the compression mechanism (21), the expansion mechanism (24), and the heat source side fan (28), thereby concurrently controlling the evaporating temperature of the refrigerant, the degree 10 of superheat of the refrigerant, and the high pressure of the refrigeration cycle.

4. The refrigeration apparatus of claim 1, wherein in heating operation, the predetermined physical value includes a degree of superheat of the 15 refrigerant at an outlet of the heat source side heat exchanger (23), and the control section (40) receives the degree of superheat of the refrigerant, and the high pressure of the refrigeration cycle as inputs, and concurrently controls the compression mechanism (21) and the expansion mechanism (24), thereby concurrently controlling the degree of superheat of the refrigerant, and the high 20 pressure of the refrigeration cycle.

5. The refrigeration apparatus of claim 1, wherein the compression mechanism includes a first compressor (21a) for sucking and compressing a low pressure refrigerant, and a second compressor (21b) for further 25 compressing and discharging the refrigerant discharged from the first compressor (21 a), 60 D08WB1 48 the expansion mechanism includes a first expansion mechanism (24) for expanding a high pressure refrigerant, and a second expansion mechanism (26) for further expanding the refrigerant expanded to an intermediate pressure refrigerant in the first expansion mechanism (24), 5 in cooling operation, the predetermined physical value includes an evaporating temperature of the refrigerant in the utilization side heat exchanger (27), a degree of superheat of the refrigerant at an outlet of the utilization side heat exchanger (27), and an intermediate pressure of the refrigeration cycle, and 10 the control section (240) receives the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, the intermediate pressure of the refrigeration cycle, and the high pressure of the refrigeration cycle as inputs, and concurrently controls the first and second compressors (21a, 21b), and the first and second expansion mechanisms (24, 26), thereby concurrently controlling the 15 evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, the intermediate pressure of the refrigeration cycle, and the high pressure of the refrigeration cycle.

6. The refrigeration apparatus of claim 1, wherein 20 the compression mechanism includes a first compressor (21 a) for sucking and compressing a low pressure refrigerant, and a second compressor (21 b) for further compressing and discharging the refrigerant discharged from the first compressor (21 a), the expansion mechanism includes a first expansion mechanism (24) for expanding a high pressure refrigerant, and a second expansion mechanism (26) for further expanding the 25 refrigerant expanded to an intermediate pressure refrigerant in the first expansion mechanism 61 D08WBI48 (24), in heating operation, the predetermined physical value includes, an evaporating temperature of the refrigerant in the heat source side heat exchanger (23), a degree of superheat of 5 the refrigerant at an outlet of the heat source side heat exchanger (23), and a gas cooler outlet temperature which is a temperature of the refrigerant at an outlet of the utilization side heat exchanger (27), and the control section (240) receives the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, the gas cooler outlet 10 temperature of the refrigerant, and the high pressure of the refrigeration cycle as inputs, and concurrently controls the first and second compressors (21a, 21b), and the first and second expansion mechanisms (24, 26), thereby concurrently controlling the evaporating temperature of the refrigerant, the degree of superheat of the refrigerant, the gas cooler outlet temperature of the refrigerant, and the high 15 pressure of the refrigeration cycle.

7. The refrigeration apparatus of claim 1, wherein a plurality ones of the utilization side heat exchanger (27a, 27b) are connected in parallel with each other, 20 the expansion mechanism includes a plurality of utilization side expansion mechanisms (26a, 26b) each corresponding to the utilization side heat exchangers (27a, 27b), and a heat source side expansion mechanism (24) provided between the utilization side heat exchangers (27a, 27b) and expansion mechanisms (26a, 26b), and the heat source side heat exchanger (23), 25 in cooling operation, 62 D08WB148 the predetermined physical value includes evaporating temperatures of the refrigerant in the utilization side heat exchangers (27a, 27b), and degrees of superheat of the refrigerant at the outlets of the utilization side heat exchangers (27a, 27b), and 5 the control section (340) receives the evaporating temperatures of the refrigerant, the degrees of superheat of the refrigerant in the utilization side heat exchangers (27a, 27b), and the high pressure of the refrigeration cycle as inputs, and concurrently controls the compression mechanism (21), the plurality of utilization side heat expansion mechanisms (26a, 26b), and the heat source side expansion 10 mechanism (24), thereby concurrently controlling the evaporating temperatures of the refrigerant, and the degrees of superheat of the refrigerant in the utilization side heat exchangers (27a, 27b), and the high pressure of the refrigeration cycle.

8. The refrigeration apparatus of claim 1, wherein 15 a plurality ones of the utilization side heat exchanger (27a, 27b) are connected in parallel with each other, the expansion mechanism includes a plurality of utilization side expansion mechanisms (26a, 26b) each corresponding to the utilization side heat exchangers (27a, 27b), and a heat source side expansion mechanism (24) provided between the utilization side heat 20 exchangers (27a, 27b) and expansion mechanisms (26a, 26b), and the heat source side heat exchanger (23), in heating operation, the predetermined physical value includes a degree of superheat of the refrigerant at an outlet of the heat source side heat exchanger (23), and gas cooler 25 outlet temperatures of the refrigerant which are temperatures of the refrigerant at 63 D08WB148 outlets of the utilization side heat exchangers (27a, 27b), and the control section (340) receives the degree of superheat of the refrigerant, the gas cooler outlet temperatures of the refrigerant in the utilization side heat exchangers (27a, 27b), and the high pressure of the refrigeration cycle as 5 inputs, and concurrently controls the compression mechanism (21), the plurality of utilization side expansion mechanisms (26a, 26b), and the heat source side expansion mechanism (24), thereby concurrently controlling the degree of superheat of the refrigerant, the gas cooler outlet temperatures of the refrigerant in the utilization side heat exchangers (27a, 27b), and the high pressure of the refrigeration 10 cycle. 64 D08WB148