JP2011075162A - Air conditioner adjustment device, and air conditioning device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioner adjustment device and an air conditioning device, reducing development load, and being economically installed. <P>SOLUTION: This air conditioner adjustment device is equipped with: a gas branch pipe 41 and a liquid branch pipe 42 connecting an existing EHP-type outdoor unit 10 and an existing GHP-type outdoor unit 20, and an indoor unit 30; gas flow rate adjustment valves 43, 44 for adjusting a flow rate of a refrigerant in a gas state between the indoor unit 30 and the outdoor units 10, 20; and fluid flow rate adjustment valves 45, 46 for adjusting a flow rate of a refrigerant in a liquid state. A control section 40a acquires model information of the outdoor units 10, 20 and air-conditioning load information of the indoor unit 30, and controls openings of the gas flow rate adjustment valves 43, 44 and the liquid flow rate adjustment valves 45, 46 so that the flow rates of the refrigerants respectively supplied to the indoor unit 30 from the outdoor units 10, 20 according to the model information and the air-conditioning load information, are equal to the flow rates of the refrigerants respectively supplied from the indoor unit 30 to the outdoor units 10, 20. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to an air conditioner adjusting device and an air conditioner.

  Conventionally, as a heat pump of an air conditioner, an electric heat pump (hereinafter also referred to as EHP) using an electric motor as a power source and a gas heat pump (hereinafter also referred to as GHP) using a gas engine are known. The EHP air conditioner has low initial cost and excellent low-load operation characteristics, but has a characteristic that the running cost is relatively high. On the other hand, the GHP air conditioner has a characteristic that running cost is low by using a relatively inexpensive gas. Moreover, the heating operation in the GHP type air conditioner can improve the heating efficiency by using exhaust heat such as high-temperature exhaust gas discharged from the gas engine as a refrigerant heating source. In addition, exhaust heat can be used for frost removal operation during heating operation, so-called defrost operation. The defrosting operation of an EHP type air conditioner generally performs cooling operation to remove frost in the outdoor unit heat exchanger, and cold air blows out from the indoor unit, which may impair the comfort of the indoor air conditioning environment Therefore, the GHP air conditioner is superior.

  However, even the GHP type air conditioner having many advantages as described above has characteristics that the initial cost is slightly high and the efficiency at the time of low load operation is poor. This is because the gas engine has a lower engine efficiency when it is rotated at a low speed (during low load operation) with a low capacity ratio, and improvement is particularly desired from the viewpoint of energy saving in recent years. Therefore, in order to complement the characteristics of the EHP and GHP air conditioners, a combination of these EHP and GHP air conditioners is known.

  For example, the air conditioner of Patent Document 1 includes a plurality (two) of compressors having different capacities, and drives one compressor having a large capacity with a gas engine and uses the exhaust heat as a refrigerant during heating operation. It has been proposed to be used for heating. In addition, it has been proposed that the other compressor having a small capacity is driven by an electric motor, and the exhaust heat of the power generation device of the power generation facility provided is used for refrigerant heating during heating operation. Then, two compressors having different capacities are connected in parallel, and the gas engine or the electric motor is driven according to the air conditioning load, or the gas engine and the electric motor are driven simultaneously.

  Further, the air conditioner of Patent Document 2 includes EHP and GHP type air conditioners that can operate independently, and these EHP and GHP type air conditioners determined according to fluctuations in the air conditioning load by the general air conditioning controller. Each air conditioner is controlled based on the air conditioning balance between the air conditioners. In this case, the general air conditioning controller can optimally control the EHP and GHP type air conditioners as a whole.

JP 2003-56931 A JP 2007-187342 A

  By the way, in the air conditioner of Patent Document 1, a compressor using an electric motor as a power source and a compressor using a gas engine as a power source coexist in the outdoor unit, and these two compressors having different capacities are arranged in parallel. In order to connect, for example, a dedicated refrigerant circuit different from the outdoor unit of a general-purpose EHP or GHP type air conditioner must be designed, for example, a refrigerant circuit is branched between the four-way valve. In this case, it is necessary to invest a large-scale development cost. Since the initial cost increases and the number of years of collection due to running merit increases, it becomes difficult to actually put it on the market.

  Further, in the air conditioner of Patent Document 2, it is described that the EHP and GHP type air conditioners are optimally controlled as a whole while continuously using the existing air conditioner. However, the EHP and GHP type air is described. An indoor unit is required for each of the harmony devices, and the refrigerant system in the part becomes two systems, which increases the construction cost.

  An object of the present invention is to provide an air conditioner adjusting device and an air conditioner that can reduce development load and can be installed economically.

  In order to solve the above-mentioned problems, the invention according to claim 1 is a gas state in which the ready-made electric heat pump type first outdoor unit and the ready-made gas heat pump type second outdoor unit are connected to the indoor unit. A gas branch pipe for flowing the refrigerant, a liquid branch pipe for connecting the first outdoor unit and the second outdoor unit, and the indoor unit to flow a refrigerant in a liquid state, and the gas branch pipe, A first gas flow rate adjusting valve and a second gas flow rate adjusting valve for adjusting a flow rate of the refrigerant in a gaseous state between the indoor unit and the first outdoor unit and the second outdoor unit; and the liquid branch pipe. A first liquid flow rate adjustment valve and a second liquid flow rate adjustment valve that adjust the flow rate of the refrigerant in the liquid state between the indoor unit, the first outdoor unit, and the second outdoor unit, the first outdoor unit, and the Model information acquisition means for acquiring model information of the second outdoor unit, and the room Air-conditioning load information acquisition means for acquiring air-conditioning load information of the unit, and refrigerants respectively supplied from the first outdoor unit and the second outdoor unit to the indoor unit according to the acquired model information and air-conditioning load information The opening degree of the first and second gas flow rate adjustment valves and the first and second gas flow rate adjusting valves so that the flow rate matches the flow rate of the refrigerant respectively supplied from the indoor unit to the first outdoor unit and the second outdoor unit. The gist of the invention is that it includes control means for controlling the opening degree of the second liquid flow rate adjusting valve.

  According to this configuration, if the air conditioner adjusting device that links the first outdoor unit and the second outdoor unit and the indoor unit are designed, etc., the ready-made product (mass-produced product) can be used. Therefore, the development load can be reduced. In addition, when an outdoor unit of an air conditioner of either one of an electric heat pump (EHP) type and a gas heat pump (GHP) type is already installed in a building (such as a building) related to air conditioning, the outdoor unit is diverted. Can be very economical. Furthermore, since it is not necessary to provide the indoor unit individually for each of the EHP type and GHP type outdoor units, the piping construction cost can be reduced accordingly.

  Here, the flow rate of the refrigerant respectively supplied from the first outdoor unit and the second outdoor unit to the indoor unit according to the acquired model information and air conditioning load information is determined from the indoor unit to the first outdoor unit. And the opening degree of the first and second gas flow rate adjustment valves and the opening of the first and second liquid flow rate adjustment valves so as to match the flow rate of the refrigerant respectively supplied (returned) to the second outdoor unit. By controlling the degree, the flow rate of refrigerant and lubricating oil (so-called refrigerating machine oil) that circulates even if air conditioning is performed in the indoor unit in cooperation with the first outdoor unit and the second outdoor unit. Can be prevented from becoming unbalanced between the first outdoor unit and the second outdoor unit.

  According to a second aspect of the present invention, there is provided an electric motor, a first compressor that is driven by the electric motor to suck in the refrigerant and compresses and discharges the sucked refrigerant, and an inlet and an outlet of the first compressor Are connected to the first switching valve for switching the refrigerant flow path during the cooling operation and the heating operation, and functions as a refrigerant condenser during the cooling operation and connected to the first switching valve. A first outdoor unit having a first outdoor unit heat exchanger that functions as an evaporator, a gas engine, a second compressor that is driven by the gas engine to suck in refrigerant and compresses and discharges the sucked refrigerant; A second switching valve that is connected to the suction port and the discharge port of the second compressor to switch the refrigerant flow path during cooling operation and heating operation, and is connected to the second switching valve to condense refrigerant during cooling operation. Function as a heater and during heating operation A second outdoor unit heat exchanger functioning as an evaporator of the medium, a second outdoor unit having a coolant circuit that exchanges heat with the exhaust heat of the gas engine and supplies the refrigerant during heating operation, and cooling operation In an air conditioner adjustment apparatus that connects an indoor unit having an indoor unit heat exchanger that functions as a refrigerant evaporator and functions as a refrigerant condenser during heating operation, the air conditioner adjustment device is connected to the first switching valve. A gas branch pipe having a first gas branch section, a second gas branch section connected to the second switching valve, and a gas collecting section connected to the indoor unit heat exchanger; and the first outdoor unit heat exchange. A liquid branch pipe having a first liquid branch portion connected to the chamber, a second liquid branch portion connected to the second outdoor unit heat exchanger, and a liquid collecting portion connected to the indoor unit heat exchanger; The indoor unit is provided in the gas branch pipe during cooling operation. The flow rate of the refrigerant in the gaseous state from the exchanger is adjusted and supplied to the first compressor through the first switching valve, and during the heating operation, the first switching valve discharged from the first compressor is passed through the first switching valve. Provided in the gas branch pipe and the first gas flow rate adjusting valve for supplying the gaseous refrigerant to the indoor unit heat exchanger, and during cooling operation, the flow rate of the gaseous refrigerant from the indoor unit heat exchanger is adjusted. The refrigerant is adjusted and supplied to the second compressor via the second switching valve, and during heating operation, the refrigerant in the gaseous state discharged from the second compressor via the second switching valve is exchanged with the indoor unit heat. A second gas flow rate adjusting valve for supplying to the unit; and a liquid branch pipe provided in the liquid branch pipe for supplying the refrigerant in the liquid state from the first outdoor unit heat exchanger to the indoor unit heat exchanger during the cooling operation. During operation, the flow rate of the liquid refrigerant from the indoor unit heat exchanger is adjusted to heat the first outdoor unit. A first liquid flow control valve for supplying to the exchanger and the liquid branch pipe, and supplying the refrigerant in the liquid state from the second outdoor unit heat exchanger to the indoor unit heat exchanger during cooling operation; During the heating operation, a second liquid flow rate adjustment valve that adjusts the flow rate of the refrigerant in the liquid state from the indoor unit heat exchanger and supplies the refrigerant to the second outdoor unit heat exchanger, the first outdoor unit, and the second outdoor unit. Model information acquisition means for acquiring model information of outdoor units, air conditioning load information acquisition means for acquiring air conditioning load information of the indoor units, and the first outdoor unit according to the acquired model information and air conditioning load information And the flow rate of the refrigerant respectively supplied from the second outdoor unit to the indoor unit matches the flow rate of the refrigerant supplied from the indoor unit to the first outdoor unit and the second outdoor unit. During operation, the first and second gas flow rate adjustments The opening control respectively, during the heating operation is summarized as further comprising a control means for controlling each of the opening degree of the first and second liquid flow control valve.

  According to this configuration, the first outdoor unit includes the electric motor, the compressor (first compressor), the four-way valve (first switching valve), and the outdoor unit heat exchanger (first outdoor unit heat exchanger). It consists of an off-the-shelf EHP-type outdoor unit that is integrated. The second outdoor unit includes the gas engine, a compressor (second compressor), a four-way valve (second switching valve), an outdoor unit heat exchanger (second outdoor unit heat exchanger), and the coolant circuit. It is comprised with the ready-made GHP type outdoor unit which integrally has. Therefore, if the air conditioner adjustment device that links the first outdoor unit, the second outdoor unit, and the indoor unit is designed, etc., it is basically developed by diverting off-the-shelf products (mass-produced products). Can reduce the load. In addition, when an outdoor unit of one of the EHP type and GHP type air conditioners has already been installed in a building (such as a building) related to air conditioning, the outdoor unit can be diverted and is extremely economical. is there. Furthermore, since it is not necessary to provide the indoor unit individually for each of the EHP type and GHP type outdoor units, the piping construction cost can be reduced accordingly.

  Here, the flow rate of the refrigerant respectively supplied from the first outdoor unit and the second outdoor unit to the indoor unit according to the acquired model information and air conditioning load information is determined from the indoor unit to the first outdoor unit. And the opening degree of the first and second gas flow rate regulating valves is controlled during the cooling operation so as to coincide with the flow rate of the refrigerant respectively supplied (returned) to the second outdoor unit, and during the heating operation. The opening degree of the first and second liquid flow rate regulating valves is controlled, so that the air conditioning in the indoor unit is performed in cooperation with the first outdoor unit and the second outdoor unit. It is possible to prevent the flow rates of the refrigerant and the lubricating oil (so-called refrigerating machine oil) from becoming unbalanced between the first outdoor unit and the second outdoor unit.

  According to a third aspect of the present invention, in the air conditioner adjusting device according to the first or second aspect, the first outdoor unit and the second outdoor unit are based on the acquired model information and air conditioning load information. The gist is that a stopping means for selectively stopping the operation is provided.

  According to this configuration, for example, during low load operation, the air conditioning efficiency can be improved by stopping the operation of the second outdoor unit (GHP type outdoor unit) by the stopping means. Further, at the time of medium load operation, it is possible to improve the air conditioning efficiency (heating efficiency) particularly during the heating operation by stopping the operation of the first outdoor unit (EHP type outdoor unit) by the stopping means. And at the time of high load operation, suitable air conditioning capability can be ensured by the cooperative operation of the first outdoor unit and the second outdoor unit.

  According to a fourth aspect of the present invention, there is provided the air conditioner adjusting apparatus according to the second aspect, wherein the first air branching unit and the second gas branching unit are arranged in the first gas branching unit and detect the pressure of the refrigerant flowing through each of them. A first atmospheric pressure sensor and a second atmospheric pressure sensor; a first hydraulic pressure sensor and a second hydraulic pressure sensor which are disposed in the first liquid branching unit and the second liquid branching unit and detect the pressure of a refrigerant flowing through each of the first liquid branching unit and the second liquid branching unit And the control means includes the first liquid branch portion and the second liquid corresponding to the refrigerant pressure detected in one and the other of the first hydraulic pressure sensor and the second hydraulic pressure sensor, respectively, during cooling operation. The flow rate of the refrigerant flowing through the branch portion flows through the first gas branch portion and the second gas branch portion corresponding to the pressure of the refrigerant detected at one and the other of the first atmospheric pressure sensor and the second atmospheric pressure sensor, respectively. To match the flow rate of the refrigerant The other opening and the other opening of the first gas flow control valve and the second gas flow control valve are respectively controlled, and detected in one and the other of the first atmospheric pressure sensor and the second atmospheric pressure sensor during heating operation, respectively. The flow rate of the refrigerant flowing through the first gas branch and the second gas branch corresponding to the pressure of the refrigerant is detected by one or the other of the first hydraulic pressure sensor and the second hydraulic pressure sensor, respectively. The opening degree of the other and one of the first liquid flow rate adjustment valve and the second liquid flow rate adjustment valve is set so as to coincide with the flow rate of the refrigerant flowing through the first liquid branch portion and the second liquid branch portion corresponding to the pressure, respectively. The gist is to control.

  According to this configuration, during cooling operation, the flow rate of the refrigerant flowing through one and the other of the first gas branching portion and the second gas branching portion cooperates with each other (the first gas branching portion and the second gas branching). This is performed by controlling the opening degree of the other and one of the first gas flow rate adjustment valve and the second gas flow rate adjustment valve related to the refrigerant flow rate adjustment of the other part. Similarly, at the time of heating operation, the flow rate of the refrigerant flowing through one and the other of the first liquid branch and the second liquid branch is equal to the other party (the other of the first liquid branch and the second liquid branch). And one of the first liquid flow rate adjustment valve and the second liquid flow rate adjustment valve according to the flow rate adjustment of the refrigerant. Accordingly, the first outdoor unit and the second outdoor unit can cooperate more closely in controlling the flow rate of the circulating refrigerant and lubricating oil, for example, the first gas flow rate to ensure only its own refrigerant flow rate. It can suppress that the opening degree of a regulating valve or a 2nd gas flow regulating valve (a 1st liquid flow regulating valve or a 2nd liquid flow regulating valve) becomes excessive.

  According to a fifth aspect of the present invention, in the air conditioner adjusting device according to the fourth aspect, the first gas flow rate adjustment valve, the second gas flow rate adjustment valve, the first liquid flow rate adjustment valve, and the second liquid. The gist is that each opening degree of the flow rate adjusting valve is set to a predetermined lower limit opening degree or more.

  According to this configuration, the opening degree of any of the first gas flow rate adjustment valve, the second gas flow rate adjustment valve, the first liquid flow rate adjustment valve, and the second liquid flow rate adjustment valve becomes too small, and It is possible to avoid restrictions on circulation and the like.

  According to a sixth aspect of the present invention, there is provided an electric motor, a first compressor that is driven by the electric motor to suck in the refrigerant and compresses and discharges the sucked refrigerant, and an inlet and an outlet of the first compressor Are connected to the first switching valve for switching the refrigerant flow path during the cooling operation and the heating operation, and functions as a refrigerant condenser during the cooling operation and connected to the first switching valve. A first outdoor unit having a first outdoor unit heat exchanger that functions as an evaporator, a gas engine, a second compressor that is driven by the gas engine to suck in refrigerant and compresses and discharges the sucked refrigerant; A second switching valve that is connected to the suction port and the discharge port of the second compressor to switch the refrigerant flow path during cooling operation and heating operation, and is connected to the second switching valve to condense refrigerant during cooling operation. Function as a heater and during heating operation A second outdoor unit heat exchanger functioning as an evaporator of the medium, a second outdoor unit having a coolant circuit that exchanges heat with the exhaust heat of the gas engine and supplies the refrigerant during heating operation, and cooling operation An indoor unit having an indoor unit heat exchanger that functions as a refrigerant evaporator during heating and functions as a refrigerant condenser during heating operation, and each of the first outdoor unit and the second outdoor unit connected to the indoor unit An air conditioner adjusting device, the air conditioner adjusting device comprising: a first gas branching unit connected to the first switching valve; a second gas branching unit connected to the second switching valve; A gas branch pipe having a gas collecting part connected to the indoor unit heat exchanger, a first liquid branch part connected to the first outdoor unit heat exchanger, and a second outdoor unit heat exchanger. The second liquid branch portion and the liquid connected to the indoor unit heat exchanger A liquid branch pipe having a joint and the gas branch pipe are provided, and during cooling operation, the flow rate of the refrigerant in the gaseous state from the indoor unit heat exchanger is adjusted and the first switching valve is used to adjust the first flow rate. A first gas flow rate adjusting valve that supplies the refrigerant in a gaseous state to the indoor unit heat exchanger via the first switching valve discharged from the first compressor during heating operation; Provided in the branch pipe, adjusts the flow rate of the refrigerant in the gaseous state from the indoor unit heat exchanger during cooling operation, and supplies the refrigerant to the second compressor via the second switching valve. A second gas flow rate adjusting valve for supplying a refrigerant in a gaseous state discharged from the second compressor to the indoor unit heat exchanger via the second switching valve; and the liquid branch pipe. Supplying the refrigerant in the liquid state from the first outdoor unit heat exchanger to the indoor unit heat exchanger, A first liquid flow rate adjustment valve that adjusts the flow rate of the refrigerant in the liquid state from the indoor unit heat exchanger and supplies the first outdoor unit heat exchanger to the first outdoor unit heat exchanger and the liquid branch pipe during cooling, At the time of supplying the refrigerant in the liquid state from the second outdoor unit heat exchanger to the indoor unit heat exchanger, and adjusting the flow rate of the refrigerant in the liquid state from the indoor unit heat exchanger during the heating operation. A second liquid flow rate adjusting valve to be supplied to the second outdoor unit heat exchanger, model information acquisition means for acquiring model information of the first outdoor unit and the second outdoor unit, and air conditioning load information of the indoor unit. The air conditioning load information acquisition means to acquire, and the flow rate of the refrigerant respectively supplied from the first outdoor unit and the second outdoor unit to the indoor unit according to the acquired model information and air conditioning load information are the indoor unit To the first outdoor unit and the second outdoor unit, respectively. The opening degree of the first and second gas flow rate adjustment valves is controlled during cooling operation, and the opening degree of the first and second liquid flow rate adjustment valves is set during heating operation. The gist of the invention is that it comprises a control means for controlling.

  According to this configuration, it is possible to provide an air conditioner that can reduce development load and can be installed economically.

  In the present invention, it is possible to provide an air conditioner adjusting device and an air conditioner that can reduce development load and can be installed economically.

The circuit diagram which shows one Embodiment of this invention. The graph which shows the relationship between an air-conditioning load and load sharing. The map which shows the relationship between an air-conditioning load and setting pressure. (A)-(d) is a map which shows the relationship between the deviation of a target pressure and an actual pressure, and an opening degree. The flowchart which shows the air-conditioning load distribution control aspect of the embodiment. The flowchart which shows the opening degree control aspect of the gas flow regulating valve of the embodiment. The flowchart which shows the opening degree control aspect of the liquid flow regulating valve of the embodiment.

DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment of the invention will be described with reference to the drawings.
FIG. 1 is a circuit diagram schematically showing an air conditioner 1 according to the present embodiment. As shown in the figure, the air conditioner 1 includes an EHP-type first outdoor unit 10 that is an off-the-shelf product (mass-produced product), and a GHP-type second outdoor unit 20 that is also an off-the-shelf product (mass-produced product). The indoor unit 30 and the air conditioner adjusting device 40 are provided.

  The first outdoor unit 10 includes an electric motor 11 and a first compressor 12 driven by the electric motor 11. The first compressor 12 sucks the refrigerant, compresses the sucked refrigerant, and sends the refrigerant to a four-way valve 14 serving as a first switching valve connected to the discharge port via a refrigerant pipe 13a.

  The four-way valve 14 is for switching the refrigerant flow path between the cooling operation and the heating operation, and is connected to the first outdoor unit heat exchanger 15 via the refrigerant pipe 13b and via the refrigerant pipe 13c. Are connected to the suction port of the first compressor 12 and further connected to the on-off valve 16 via the refrigerant pipe 13d. The first outdoor unit heat exchanger 15 functions as a refrigerant condenser during the cooling operation and functions as a refrigerant evaporator during the heating operation, and is connected to the open / close valve 17 via the refrigerant pipe 13e. . In the vicinity of the first outdoor unit heat exchanger 15, a fan 18 for blowing air for promoting heat exchange with the outside air is installed.

  The second outdoor unit 20 includes a gas engine 21 and a second compressor 22 driven by the gas engine 21. The second compressor 22 sucks the refrigerant, compresses the sucked refrigerant, and sends the refrigerant to a four-way valve 24 as a second switching valve connected to the discharge port via the refrigerant pipe 23a.

  The four-way valve 24 is for switching the refrigerant flow path between the cooling operation and the heating operation, and is connected to the second outdoor unit heat exchanger 25 through the refrigerant pipe 23b and through the refrigerant pipe 23c. Are connected to the suction port of the second compressor 22 and further connected to the on-off valve 26 via the refrigerant pipe 23d. The second outdoor unit heat exchanger 25 functions as a refrigerant condenser during the cooling operation and functions as a refrigerant evaporator during the heating operation, and is connected to the on-off valve 27 via the refrigerant pipe 23e. . In the vicinity of the second outdoor unit heat exchanger 25, a blower fan 28 is installed to promote heat exchange with the outside air. Moreover, between the gas engine 21 and the 2nd outdoor unit heat exchanger 25, it heat-exchanges with the exhaust heat of the gas engine 21, and is used for the heating of a refrigerant | coolant in the 2nd outdoor unit heat exchanger 25 at the time of heating operation. A coolant circuit 29 is configured.

  The indoor unit 30 includes an indoor unit heat exchanger 31 and an expansion valve 33 connected to the indoor unit heat exchanger 31 via a refrigerant pipe 32a. The indoor unit heat exchanger 31 functions as a refrigerant evaporator during cooling operation and functions as a refrigerant condenser during heating operation. In the vicinity of the indoor unit heat exchanger 31, a blower fan 34 is installed to promote heat exchange with indoor air.

  The air conditioner adjusting device 40 includes a gas branch pipe 41 for circulating a refrigerant in a gaseous state between the first and second outdoor units 10 and 20 and the indoor unit 30. The gas branch pipe 41 is connected to the first and second gas branch portions 41 a and 41 b connected to the on-off valves 16 and 26 (four-way valves 14 and 24), respectively, and the indoor unit heat exchanger 31. It has a gas collecting part 41c. In addition, the air conditioner adjustment device 40 includes a liquid branch pipe 42 for circulating a liquid refrigerant between the first and second outdoor units 10 and 20 and the indoor unit 30. The liquid branch pipe 42 includes a first liquid branch portion 42a and a second liquid branch portion 42b connected to the on-off valves 17 and 27 (first and second outdoor unit heat exchangers 15 and 25), respectively, and the expansion valve. A liquid collecting portion 42c connected to the first side 33.

  In the first and second gas branch portions 41a and 41b, a first gas flow rate adjustment valve 43 and a second gas flow rate adjustment valve 44, which are linear adjustment valves, are disposed. The first gas flow rate adjusting valve 43 adjusts the flow rate of the refrigerant in the gaseous state from the indoor unit heat exchanger 31 during the cooling operation, and supplies it to the first compressor 12 through the on-off valve 16 and the four-way valve 14, During the heating operation, the gaseous refrigerant discharged from the first compressor 12 through the four-way valve 14 and the on-off valve 16 is supplied to the indoor unit heat exchanger 31. Similarly, the second gas flow rate adjustment valve 44 adjusts the flow rate of the refrigerant in the gaseous state from the indoor unit heat exchanger 31 during the cooling operation, and is supplied to the second compressor 22 via the on-off valve 26 and the four-way valve 24. In the heating operation, the refrigerant in the gaseous state discharged from the second compressor 22 via the four-way valve 24 and the on-off valve 26 is supplied to the indoor unit heat exchanger 31.

  On the other hand, a first liquid flow rate adjustment valve 45 and a second liquid flow rate adjustment valve 46, which are linear adjustment valves, are disposed in the first and second liquid branch portions 42a and 42b. The first liquid flow rate adjustment valve 45 supplies the refrigerant in the liquid state via the on-off valve 17 from the first outdoor unit heat exchanger 15 to the indoor unit heat exchanger 31 via the expansion valve 33 during the cooling operation. During the heating operation, the flow rate of the refrigerant in the liquid state from the indoor unit heat exchanger 31 through the expansion valve 33 is adjusted and supplied to the first outdoor unit heat exchanger 15 through the on-off valve 17. Similarly, the second liquid flow rate adjusting valve 46 supplies the refrigerant in the liquid state via the open / close valve 27 from the second outdoor unit heat exchanger 25 to the indoor unit heat exchanger 31 via the expansion valve 33 during the cooling operation. In the heating operation, the flow rate of the refrigerant in the liquid state from the indoor unit heat exchanger 31 through the expansion valve 33 is adjusted and supplied to the second outdoor unit heat exchanger 25 through the on-off valve 27.

  Here, the operation related to the air conditioning of the air conditioning apparatus 1 will be described on the assumption that both the EHP and GHP outdoor units 10 and 20 are driven. In addition, the flow of the refrigerant | coolant at the time of each operation | movement of cooling and heating is represented by the solid line arrow and the broken line arrow.

  First, during cooling operation, the refrigerant that has exited the discharge ports of the compressors 12 and 22 of the outdoor units 10 and 20 passes through the four-way valves 14 and 24 and then functions as outdoor unit heat exchangers 15 and 25 that function as condensers. Led to. In the outdoor unit heat exchangers 15 and 25, the refrigerant is deprived of heat by outdoor air (outside air) and condensed and liquefied. Thereafter, the refrigerant guided to the first and second liquid branch portions 42 a and 42 b of the liquid branch pipe 42 merges at the liquid collecting portion 42 c in the air conditioner adjustment device 40 and is guided to the indoor unit 30. The refrigerant guided to the indoor unit 30 is decompressed by the electronic expansion valve 33, and in the indoor unit heat exchanger 31 functioning as an evaporator, the heat of the indoor air is taken and vaporized. Thereafter, the refrigerant guided to the gas collecting part 41c of the gas branch pipe 41 is branched in the first and second gas branching parts 41a and 41b in the air conditioner adjusting device 40, and is passed through the four-way valves 14 and 24. Return to the suction ports of the compressors 12 and 22. Through the above process, the room is cooled.

  On the other hand, during the heating operation, the refrigerant that has exited the discharge ports of the compressors 12 and 22 of the outdoor units 10 and 20 passes through the four-way valves 14 and 24, and then the first and second gas branch portions of the gas branch pipe 41. 41 a and 41 b, merge at the gas collecting portion 41 c in the air conditioner adjustment device 40, and are guided to the indoor unit 30. The refrigerant releases heat into the indoor air in the indoor unit heat exchanger 31 functioning as a condenser, and condenses and liquefies. Thereafter, the refrigerant depressurized in the electronic expansion valve 33 is guided to the liquid collecting portion 42c of the liquid branch pipe 42, and is diverted in the first and second liquid branch portions 42a and 42b in the air conditioner adjusting device 40 to be outdoors. It is guided to the machine heat exchangers 15 and 25. The refrigerant absorbs and vaporizes the heat of the outdoor air in the outdoor unit heat exchangers 15 and 25 that function as an evaporator. At this time, the coolant circuit 29 that exchanges heat with the exhaust heat of the gas engine 21 is used to heat the refrigerant. Thereafter, the refrigerant from the outdoor unit heat exchangers 15 and 25 through the four-way valves 14 and 24 returns to the suction ports of the compressors 12 and 22. Through the above process, the room is heated.

  The first and second gas branch portions 41a and 41b are provided with a first atmospheric pressure sensor 47 and a second atmospheric pressure sensor 48 for detecting the pressure (atmospheric pressure) P1 and P2 of the refrigerant flowing therethrough. . The first and second liquid branch portions 42a and 42b are provided with a first hydraulic pressure sensor 49 and a second hydraulic pressure sensor 50 for detecting pressures (fluid pressures) P3 and P4 of the refrigerant flowing through the first and second liquid branch portions 42a and 42b, respectively. Has been.

  Next, the electrical configuration of the air conditioner 1 will be described. As shown in FIG. 1, the first outdoor unit 10, the second outdoor unit 20, the indoor unit 30, and the air conditioner adjusting device 40 are, for example, control units 10a, 20a, 30a, 40a mainly composed of a microcomputer. Each is provided. The control units 10a and 20a drive and control the corresponding compressors 12 and 22 and the fans 18 and 28, respectively. The control unit 30a controls and drives the expansion valve 33 and the fan 34 and the air conditioning load. Calculate and store. And the control part 40a is electrically connected with these control parts 10a, 20a, and 30a, and is mutually cooperated. When connecting the control units 10a, 20a, and 30a to the control unit 40a, the existing input / output ports are used for the control units 10a, 20a, and 30a, and are basically off-the-shelf first and second outdoor units. Machines 10, 20, etc. have not been refurbished.

  And the control part 40a which comprises a control means acquires the model information (rated load information etc.) of the 1st and 2nd outdoor units 10 and 20 from the control parts 10a and 20a (model information acquisition means), and a control part The air conditioning load information of the indoor unit 30 in operation is acquired from 30a (air conditioning load information acquisition means). The air conditioning load information includes the cooling / warming information during either the cooling or heating operation cycle. The air conditioning load is calculated based on, for example, the difference between the indoor temperature where the indoor unit 30 is installed and the set temperature. In particular, when there are a plurality of indoor units 30 connected to the air conditioner adjustment device 40, the total air conditioning load calculated in each indoor unit 30 is obtained.

  The control unit 40a controls the control units 10a and 20a to drive at least one of the first and second outdoor units 10 and 20 based on the acquired model information and air conditioning load information. FIG. 2 shows the air conditioning load and the first and second outdoor units 10, 20 when the air conditioning load when both the first and second outdoor units 10, 20 are driven at the rated maximum capacity (rated load) is 100%. It is a graph which shows the relationship with no load sharing. As shown in the figure, predetermined values A and B (A <B) are set as switching points of the air conditioning load in the load sharing mode of the first and second outdoor units 10 and 20. The predetermined value A (%) is set to an optimum value that can suppress the low-load operation and improve the operation efficiency in the GHP-type second outdoor unit 20 corresponding to the acquired model information. . The predetermined value B is set based on the rated load of the GHP-type second outdoor unit 20 corresponding to the acquired model information. When the air conditioning load is a low load less than the predetermined value A, the control unit 40a controls the control units 10a and 20a to drive only the EHP type first outdoor unit 10 in consideration of the excellent load characteristics. (Stop means). In addition, when the air conditioning load is a medium load that is greater than or equal to the predetermined value A and less than the predetermined value B, the control unit 40a is configured to control only the second HPHP outdoor unit 20 in consideration of the excellent running cost. 20a is controlled (stopping means). Further, when the air conditioning load is a high load of a predetermined value B or more, in order to ensure sufficient air conditioning capacity, the control unit 40a controls the EHP type and GHP type outdoor units 10 and 20 to drive in parallel. 10a and 20a are controlled.

  When the outdoor units 10 and 20 are driven, the control unit 40a transmits an instruction signal indicating load sharing and operation / stop of the outdoor units 10 and 20 based on the acquired model information and air conditioning load information. 10a and 20a. The control units 10a and 20a, which are instructed to operate by the instruction signal, drive-control the compressors 12 and 22 so as to secure the load sharing. At this time, the control units 10a and 20a simultaneously switch the flow paths of the four-way valves 14 and 24 depending on which of the cooling and heating operation cycles is being performed. In addition, the control units 10 a and 20 a instructed to stop by the instruction signal stop the drive control of the compressors 12 and 22.

  Here, the controller 40a includes the first and second gas flow rate adjustment valves 43 and 44, the first and second liquid flow rate adjustment valves 45 and 46, the first and second atmospheric pressure sensors 47 and 48, and the first and second pressure flow rate adjustment valves 45 and 46. The two hydraulic pressure sensors 49 and 50 are also electrically connected. Hereinafter, the opening degree control mode of the first and second gas flow rate adjustment valves 43 and 44 and the first and second liquid flow rate adjustment valves 45 and 46 by the control unit 40a according to the drive mode of the outdoor units 10 and 20 will be described. To do.

  First, when only the EHP type first outdoor unit 10 is driven, the opening degree of the first gas flow rate adjustment valve 43 and the first liquid flow rate adjustment valve 45 is set in order to circulate the refrigerant of the first outdoor unit 10. Both are set to “100%” (fully open), and the second gas flow rate adjustment valve 44 and the second liquid flow rate adjustment valve 46 are opened so that the refrigerant of the GHP type second outdoor unit 20 does not leak to the indoor unit 30 side. Both degrees are set to “0%” (fully closed). When only the GHP type second outdoor unit 20 is driven, the opening degree of the second gas flow rate adjustment valve 44 and the second liquid flow rate adjustment valve 46 is set to circulate the refrigerant of the second outdoor unit 20. Both are set to “100%” and the opening amounts of the first gas flow rate adjustment valve 43 and the first liquid flow rate adjustment valve 45 are both set so that the refrigerant of the EHP type first outdoor unit 10 does not leak to the indoor unit 30 side. Set to “0%”.

  Further, when both the EHP type and GHP type outdoor units 10 and 20 are driven, the flow rate of the refrigerant supplied from each of the outdoor units 10 and 20 to the indoor unit 30 in accordance with the load sharing described above is determined by the indoor unit. The first and second gas flow rate adjusting valves 43 and 44, and the first and second liquid flow rate adjusting valves 45 and 46 so as to match the flow rate of the refrigerant supplied (returned) to the outdoor units 10 and 20 from 30. To control the opening degree. This is because when the air conditioning in the indoor unit 30 is performed in cooperation with both the outdoor units 10 and 20, the flow rate (circulation amount) of the circulating refrigerant and lubricating oil (refrigerating machine oil) is between these outdoor units 10 and 20. This is to suppress imbalance.

  That is, for example, during the cooling operation, the controller 40a sets both the opening degrees of the first and second liquid flow rate adjusting valves 45 and 46 to “100%”. As a result, the refrigerant having a flow rate controlled by each of the outdoor units 10 and 20 according to the load sharing is merged in the liquid branch pipe 42 (liquid collecting portion 42c) without being adjusted and supplied to the indoor unit 30 side. Is done. And the control part 40a is divided so that the refrigerant | coolant of the flow volume supplied to the indoor unit 30 may be branched by the gas branch pipe 41 (1st and 2nd gas branch part 41a, 41b), and returns to each outdoor unit 10 and 20 again. The opening degree of the first and second gas flow rate adjusting valves 43 and 44 is controlled. In this case, the control unit 40a controls the first and second gas flow rate adjusting valves 43 and 44 so that the pressures P1 and P2 detected by the first and second atmospheric pressure sensors 47 and 48 coincide with the target pressures Pt1 and Pt2, respectively. To control the opening degree.

  Here, “target pressure Pt1” and “target pressure Pt2” are set from the map shown in FIG. 3 based on the air conditioning load (%) corresponding to each load sharing for the first outdoor unit 10 and the second outdoor unit 20. It is calculated by obtaining the pressures Ps1, Ps2. That is, the target pressure Pt1 is a value obtained by subtracting the set pressure Ps1 from the pressure P3, and the target pressure Pt2 is a value obtained by subtracting the set pressure Ps2 from the pressure P4. The set pressures Ps1 and Ps2 are used for conversion so that the flow rate of the refrigerant corresponding to the pressures P1 and P2 in the gas state is equal to the flow rate of the refrigerant corresponding to the pressures P3 and P4 in the liquid state. The air conditioning load (%) corresponding to the load sharing is set to increase as the load increases. This is because, as the air conditioning load (%) corresponding to the load sharing increases, the flow rate of the refrigerant supplied from the outdoor units 10 and 20 to the indoor unit 30 increases, and accordingly, the pressures P3 and P4 are largely corrected accordingly. It is to do. Each set pressure Ps1, Ps2 is set so as to increase as the rated load of the corresponding outdoor unit 10, 20 increases. This is because the higher the air conditioning capacity of the outdoor units 10 and 20, the larger the flow rate of refrigerant that can be supplied to the indoor unit 30 by the outdoor units 10 and 20, so that the pressures P 3 and P 4 are greatly corrected accordingly. Because.

  When the pressure P1 is equal to or higher than the target pressure Pt1, the control unit 40a adjusts the first gas flow rate so as to coincide with the opening degree A1 calculated based on the target pressure Pt2 and the deviation D2 (= Pt2-P2) of the pressure P2. The valve 43 is controlled. FIG. 4A is a map showing the relationship between the deviation D2 and the opening degree A1. As shown in the figure, the opening degree A1 is set so as to decrease as the deviation D2 increases with “100%” as the upper limit, and is held at a predetermined minimum opening degree Am1 above a predetermined deviation Da2. . That is, the opening degree A1 basically becomes smaller as the pressure P2 becomes smaller than the target pressure Pt2, that is, the first outdoor unit 10 side becomes smaller as the flow rate of the refrigerant diverted to the second outdoor unit 20 side becomes insufficient. The first gas flow rate adjusting valve 43 is set to be closed in order to suppress the flow rate of the refrigerant diverted into the first flow rate. Note that the deviation D2 related to the circulation (return) of the refrigerant on the second outdoor unit 20 side in the control of the opening degree A1 of the first gas flow rate adjustment valve 43 in this way is the refrigerant that returns to the outdoor unit 20 side. This is to prevent the opening degree A1 of the first gas flow rate adjustment valve 43 from being excessively controlled without considering the flow rate of the refrigerant, that is, the flow rate of the refrigerant returning to the first outdoor unit 10 side from being excessive. On the other hand, when the pressure P1 is less than the target pressure Pt1, the control unit 40a controls this so that the opening degree of the first gas flow rate adjustment valve 43 is increased by a predetermined incremental amount ΔG (%).

  Similarly, when the pressure P2 is equal to or higher than the target pressure Pt2, the control unit 40a sets the second gas flow rate so as to coincide with the opening degree A2 calculated based on the target pressure Pt1 and the deviation D1 (= Pt1-P1) of the pressure P1. The regulating valve 44 is controlled. FIG. 4B is a map showing the relationship between the deviation D1 and the opening A2. As shown in the figure, the opening A2 is set to become smaller as the deviation D1 increases with “100%” as the upper limit, and is held at a predetermined minimum opening Am2 at a predetermined deviation Da1 or more. . That is, the opening A2 is basically such that the pressure P1 becomes smaller as the pressure P1 becomes smaller than the target pressure Pt1, that is, the second outdoor unit 20 side as the flow rate of the refrigerant diverted to the first outdoor unit 10 side becomes insufficient. The second gas flow rate adjustment valve 44 is set to be closed in order to suppress the flow rate of the refrigerant that is diverted to the first gas flow rate. On the other hand, when the pressure P2 is less than the target pressure Pt2, the control unit 40a controls the second gas flow rate adjustment valve 44 so that the opening degree of the second gas flow rate adjustment valve 44 is increased by a predetermined incremental amount ΔG (%).

  Moreover, at the time of heating operation, the control part 40a makes both the opening degree of the 1st and 2nd gas flow control valves 43 and 44 "100%". Thereby, the refrigerant | coolant of the flow volume controlled by each outdoor unit 10 and 20 according to load sharing is merged with the gas branch pipe 41 (gas gathering part 41c) as it is, without adjusting flow volume, and is supplied to the indoor unit 30 side. Is done. Then, the control unit 40a causes the refrigerant at the flow rate supplied to the indoor unit 30 to be diverted by the liquid branch pipe 42 (first and second liquid branch units 42a and 42b) and returned to the outdoor units 10 and 20 again. The opening degree of the first and second liquid flow rate adjusting valves 45 and 46 is controlled. In this case, the control unit 40a includes the first and second liquid flow rate adjustment valves 45, so that the pressures P3, P4 detected by the first and second hydraulic pressure sensors 49, 50 coincide with the target pressures Pt3, Pt4, respectively. The opening of 46 is controlled.

  Here, the “target pressure Pt3” and the “target pressure Pt4” are based on the air-conditioning load (%) corresponding to the load sharing for each of the first outdoor unit 10 and the second outdoor unit 20, and the map shown in FIG. Is calculated by obtaining set pressures Ps3 and Ps4. That is, the target pressure Pt3 is a value obtained by subtracting the set pressure Ps3 from the pressure P1, and the target pressure Pt4 is a value obtained by subtracting the set pressure Ps4 from the pressure P2. The set pressures Ps3 and Ps4 are used for conversion so that the flow rate of the refrigerant corresponding to the pressures P1 and P2 in the gas state and the flow rate of the refrigerant corresponding to the pressures P3 and P4 in the liquid state are equal to each other. The same is true.

  When the pressure P3 is equal to or higher than the target pressure Pt3, the control unit 40a adjusts the first liquid flow rate so as to coincide with the opening A3 calculated based on the target pressure Pt4 and the deviation D4 (= Pt4-P4) of the pressure P4. The valve 45 is controlled. FIG. 4C is a map showing the relationship between the deviation D4 and the opening A3. As shown in the figure, the opening A3 is set so as to decrease as the deviation D4 increases with the upper limit being “100%”, and is held at a predetermined minimum opening Am3 at a predetermined deviation Da4 or more. . That is, the opening A3 basically becomes smaller as the pressure P4 becomes smaller than the target pressure Pt4, that is, as the flow rate of refrigerant diverted to the second outdoor unit 20 becomes insufficient, the first outdoor unit 10 side becomes smaller. The first liquid flow rate adjustment valve 45 is set to be closed in order to suppress the flow rate of the refrigerant diverted into the first flow rate. On the other hand, when the pressure P3 is less than the target pressure Pt3, the controller 40a controls the opening of the first liquid flow rate adjustment valve 45 so as to increase by a predetermined incremental amount ΔL (%).

  Similarly, when the pressure P4 is equal to or higher than the target pressure Pt4, the control unit 40a causes the second liquid flow rate to coincide with the opening A4 calculated based on the target pressure Pt3 and the deviation D3 (= Pt3-P3) of the pressure P3. The regulating valve 46 is controlled. FIG. 4D is a map showing the relationship between the deviation D3 and the opening A4. As shown in the figure, the opening A4 is set so as to decrease as the deviation D3 increases with “100%” as an upper limit, and is held at a predetermined minimum opening Am4 with a predetermined deviation Da3 or more. . That is, the opening A4 is basically such that the pressure P3 becomes smaller as the pressure P3 becomes smaller than the target pressure Pt3, that is, the second outdoor unit 20 side as the flow rate of the refrigerant diverted to the first outdoor unit 10 side becomes insufficient. The second liquid flow rate adjusting valve 46 is set to be closed in order to suppress the flow rate of the refrigerant diverted into the first flow rate. On the other hand, when the pressure P4 is less than the target pressure Pt4, the control unit 40a controls the second liquid flow rate adjustment valve 46 so that the opening degree of the second liquid flow rate adjustment valve 46 is increased by a predetermined incremental amount ΔL (%).

  As described above, when both the EHP type and GHP type outdoor units 10 and 20 are driven, the flow rate of the refrigerant supplied from the outdoor units 10 and 20 to the indoor unit 30 is changed from the indoor unit 30 to the outdoor units 10 and 20. 20 is controlled so as to match the flow rate of the refrigerant supplied (returned) to the refrigerant, and the flow rate of the circulating refrigerant and lubricating oil (refrigeration oil) is suppressed from being unbalanced between the outdoor units 10 and 20. The

Next, the air conditioning control mode in the present embodiment will be described collectively.
FIG. 5 is a flowchart showing an air conditioning load distribution control mode by the control unit 40a. As shown in the figure, when the processing shifts to this routine, first, the air conditioning load level (see FIG. 2) in the corresponding operation cycle (cooling or heating operation) is determined (S1). When it is determined that the low load operation is being performed, an instruction is given to the control units 10a and 20a so that only the EHP type first outdoor unit 10 is driven (S2). If it is determined that the medium load operation is being performed, an instruction is given to the control units 10a and 20a so that only the GHP-type second outdoor unit 20 is driven (S3). Further, when it is determined that the high load operation is being performed, an instruction is given to the control units 10a and 20a so that the EHP type and GHP type outdoor units 10 and 20 are driven (S4). Then, the subsequent processing is temporarily terminated.

  FIG. 6 is a flowchart showing how the first and second gas flow rate adjusting valves 43 and 44 are controlled by the control unit 40a when the EHP and GHP outdoor units 10 and 20 are driven. FIG. 7 is a flowchart showing the opening control mode of the first and second liquid flow rate adjusting valves 45 and 46 by the control unit 40a. Each process is repeatedly executed by, for example, a scheduled interruption every predetermined time.

  As shown in FIG. 6, when the processing shifts to this routine, first, an operation cycle (cooling or heating) is determined (S11). When it is determined that the vehicle is operating in the cooling cycle, the target pressures Pt1 and Pt2 are calculated (S12). Next, it is determined whether or not the pressure P1 is equal to or higher than the target pressure Pt1 (S13). When the pressure P1 is determined to be equal to or higher than the target pressure Pt1, it is further determined whether or not the pressure P2 is equal to or higher than the target pressure Pt2 (S14). ). When it is determined in S13 that the pressure P1 is less than the target pressure Pt1, it is further determined whether or not the pressure P2 is equal to or higher than the target pressure Pt2 (S15).

  When it is determined in S14 that the pressure P2 is equal to or higher than the target pressure Pt2, the opening degrees A1 and A2 of the first and second gas flow rate adjusting valves 43 and 44 are respectively calculated (see FIG. 4), and the opening degrees A1 and A2 The first and second gas flow rate adjusting valves 43 and 44 are controlled so as to coincide with each other (S16). When it is determined in S14 that the pressure P2 is less than the target pressure Pt2, the opening A1 of the first gas flow rate adjustment valve 43 is calculated and the first gas flow rate adjustment valve 43 is controlled so as to coincide with the opening degree A1. At the same time, the opening degree of the second gas flow rate adjustment valve 44 is controlled to increase by the gradually increasing amount ΔG (%) (S17).

  On the other hand, when it is determined in S15 that the pressure P2 is equal to or higher than the target pressure Pt2, the opening degree of the first gas flow rate adjustment valve 43 is controlled to increase by the gradually increasing amount ΔG (%) and the second gas flow rate adjustment is performed. The opening degree A2 of the valve 44 is calculated, and the second gas flow rate adjusting valve 44 is controlled so as to coincide with the opening degree A2 (S18). When it is determined in S15 that the pressure P2 is less than the target pressure Pt2, the opening degree of the first and second gas flow rate adjusting valves 43, 44 is controlled so as to increase by the gradually increasing amount ΔG (%), respectively ( S19).

  If it is determined in S11 that the heating cycle is in operation, both the first and second gas flow rate adjusting valves 43 and 44 are set to fully open (S20). When the opening degree control of any one of S16 to S20 is executed, the subsequent processing is once ended.

  Further, as shown in FIG. 7, when the processing shifts to this routine, first, an operation cycle (cooling or heating) is determined (S21). When it is determined that the vehicle is operating in the heating cycle, the target pressures Pt3 and Pt4 are calculated (S22). Next, it is determined whether or not the pressure P3 is equal to or higher than the target pressure Pt3 (S23). When it is determined that the pressure P3 is equal to or higher than the target pressure Pt3, it is further determined whether or not the pressure P4 is equal to or higher than the target pressure Pt4 (S24). ). When it is determined in S23 that the pressure P3 is less than the target pressure Pt3, it is further determined whether or not the pressure P4 is equal to or higher than the target pressure Pt4 (S25).

  When it is determined in S24 that the pressure P4 is equal to or higher than the target pressure Pt4, the opening degrees A3 and A4 of the first and second liquid flow rate adjusting valves 45 and 46 are respectively calculated (see FIG. 4), and the opening degrees A3 and A4 are calculated. The first and second liquid flow rate adjusting valves 45 and 46 are controlled so as to coincide with each other (S26). When it is determined in S24 that the pressure P4 is less than the target pressure Pt4, the opening degree A3 of the first liquid flow rate adjustment valve 45 is calculated and the first liquid flow rate adjustment valve 45 is controlled so as to match the opening degree A3. At the same time, the opening degree of the second liquid flow rate adjusting valve 46 is controlled to increase by the incremental amount ΔL (%) (S27).

  On the other hand, when it is determined in S25 that the pressure P4 is equal to or higher than the target pressure Pt4, the opening degree of the first liquid flow rate adjustment valve 45 is controlled to increase by the incremental amount ΔL (%) and the second liquid flow rate adjustment is performed. The opening A4 of the valve 46 is calculated, and the second liquid flow rate adjustment valve 46 is controlled so as to coincide with the opening A4 (S28). When it is determined in S25 that the pressure P4 is less than the target pressure Pt4, the opening degree of the first and second liquid flow rate adjusting valves 45, 46 is controlled to increase by the incremental amount ΔL (%), respectively ( S29).

  If it is determined in S21 that the cooling cycle is in operation, both the first and second liquid flow rate adjusting valves 45 and 46 are set to fully open (S30). When the opening degree control of any one of S26 to S30 is executed, the subsequent processing is once ended.

As described above in detail, according to the present embodiment, the following effects can be obtained.
(1) In this embodiment, the 1st outdoor unit 10 integrates the electric motor 11, the compressor (1st compressor 12), the four-way valve 14, and the outdoor unit heat exchanger (1st outdoor unit heat exchanger 15). It is composed of a ready-made EHP outdoor unit. The second outdoor unit 20 includes a gas engine 21, a compressor (second compressor 22), a four-way valve 24, an outdoor unit heat exchanger (second outdoor unit heat exchanger 25), and a coolant circuit 29. It is composed of an off-the-shelf GHP outdoor unit. Therefore, if the air conditioner adjustment device 40 that links the first and second outdoor units 10 and 20 and the indoor unit 30 is designed, etc., the developed product can be basically utilized by diverting the ready-made product (mass-produced product). The load can be reduced and the development cost can be reduced. Since the initial cost is reduced and the number of years of recovery due to running merit is shortened, it becomes easier to actually put it on the market. In addition, when an outdoor unit of one of the EHP type and GHP type air conditioners has already been installed in a building (such as a building) related to air conditioning, the outdoor unit can be diverted and is extremely economical. is there. Furthermore, since it is not necessary to provide the indoor unit 30 for each of the EHP type and GHP type outdoor units 10 and 20, it is possible to reduce the cost and the piping construction cost accordingly. Furthermore, since the refrigerant pipes (the gas collecting part 41c and the liquid collecting part 42c) connecting the indoor unit 30 and the air conditioner adjusting device 40 may be one system, the construction cost can be reduced.

  Here, the flow rate of the refrigerant respectively supplied from the first and second outdoor units 10 and 20 to the indoor unit 30 according to the acquired model information and air conditioning load information by the control unit 40a is changed from the indoor unit 30 to the first. During the cooling operation, the opening degree of the first and second gas flow rate adjusting valves 43 and 44 is controlled so as to match the flow rate of the refrigerant supplied (returned) to the first and second outdoor units 10 and 20, respectively. During the heating operation, the opening degree of the first and second liquid flow rate adjusting valves 45 and 46 is controlled, so that the air conditioning in the indoor unit 30 is performed in cooperation with the first and second outdoor units 10 and 20. Even so, it is possible to suppress the flow of the circulating refrigerant and the lubricating oil from being unbalanced between the first and second outdoor units 10 and 20, and thus the first and second compressors 12 and 22. This performance can be suitably maintained.

  (2) In this embodiment, for example, during low load operation, the air conditioning efficiency can be improved by stopping the operation of the second outdoor unit 20 (GHP type outdoor unit). Further, during medium load operation, the running cost can be suppressed by stopping the operation of the first outdoor unit 10 (EHP type outdoor unit), and in particular, the air conditioning efficiency (heating efficiency) during the heating operation can be improved. it can. And at the time of high load operation, suitable air conditioning capability can be ensured by the cooperative operation of the first and second outdoor units 10 and 20.

  (3) In the present embodiment, during the cooling operation, the flow rate of the refrigerant flowing through one and the other of the first and second gas branch portions 41a and 41b is the same as the other party (the first and second gas branch portions 41a and 41b). The other and one of the first and second gas flow rate adjusting valves 43 and 44 relating to the refrigerant flow rate adjustment are performed by controlling the opening degrees A2 and A1 of the first and second gas flow rate adjustment valves 43 and 44. Similarly, during the heating operation, the flow rate of the refrigerant flowing through one and the other of the first and second liquid branch portions 42a and 42b cooperates with each other (the other and one of the first and second liquid branch portions 42a and 42b). This is performed by controlling the opening degrees A4 and A3 of the other and one of the first and second liquid flow rate adjusting valves 45 and 46 relating to the flow rate adjustment of the refrigerant. Therefore, the first and second outdoor units 10 and 20 can cooperate more closely in controlling the flow rate of the circulating refrigerant and lubricating oil, for example, the first gas flow rate adjustment to ensure only the refrigerant flow rate of itself. It is possible to prevent the opening degree of the valve 43 or the second gas flow rate adjustment valve 44 (the first liquid flow rate adjustment valve 45 or the second liquid flow rate adjustment valve 46) from becoming excessive.

  (4) In the present embodiment, the opening degrees A1 to A4 of the first gas flow rate adjustment valve 43, the second gas flow rate adjustment valve 44, the first liquid flow rate adjustment valve 45, and the second liquid flow rate adjustment valve 46 are predetermined. By setting the minimum opening (lower opening) Am1 to Am4 or higher, it is possible to avoid any of the openings A1 to A4 from becoming too small and restricting the circulation of the refrigerant.

  (5) In the present embodiment, when the second outdoor unit 20 is stopped due to the low load operation, the second gas flow rate adjustment valve 44 and the second liquid flow rate adjustment valve 46 corresponding to the second outdoor unit 20 are all When the first outdoor unit 10 is stopped during the middle load operation and the first outdoor unit 10 is stopped, the first gas flow rate adjustment valve 43 and the first liquid flow rate adjustment valve 45 corresponding to the first outdoor unit 10 are fully closed. By doing so, it is possible to reliably prevent the refrigerant from entering and exiting the stopped first outdoor unit 10 or the second outdoor unit 20, for example, the refrigerant of the outdoor units 10 and 20 leaks to the indoor unit 30 side and the flow rate It is possible to prevent a shortage.

  (6) In this embodiment, the control part 40a of the air conditioner adjustment device 40 acquires each model information only by electrically connecting with the control parts 10a and 20a of the ready-made outdoor units 10 and 20. These can be controlled.

  (7) In this embodiment, it is not necessary to operate the second outdoor unit 20 in the intermediate period (for example, April to May, October to November) when the air conditioning load is reduced, thereby reducing the operation time of the gas engine 21. Therefore, the maintenance cost can be reduced and the life of the second outdoor unit 20 can be extended.

(8) In the present embodiment, it is possible to provide the air conditioner 1 that can reduce the development load and can be installed economically.
In addition, you may change the said embodiment as follows.

  In the above-described embodiment, during the cooling operation, the flow rate of the refrigerant flowing through one and the other of the first and second gas branch portions 41a and 41b is set to the first and second gas flow rate adjusting valves 43 related to the flow rate adjustment of the refrigerant. , 44 and the other opening degree A1, A2 may be controlled. Similarly, during the heating operation, the flow rate of the refrigerant flowing through one and the other of the first and second liquid branch portions 42a and 42b is set to be the same as that of the first and second liquid flow rate adjustment valves 45 and 46 related to the flow rate adjustment of the own refrigerant. You may carry out by control of one and the other opening degree A3, A4. In this case, the opening degrees A1 to A4 of the first gas flow rate adjustment valve 43, the second gas flow rate adjustment valve 44, the first liquid flow rate adjustment valve 45, and the second liquid flow rate adjustment valve 46 are set so as not to become excessive. It is preferable to regulate the maximum opening (upper limit opening) or less.

In the embodiment, the indoor units 30 connected to the first and second outdoor units 10 and 20 via the air conditioner adjustment device 40 may be a plurality of units connected in parallel.
Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.

In the air conditioner adjusting device according to claim 3,
The control means is stopped by the stop means, the first gas flow rate adjustment valve corresponding to the first outdoor unit and the first liquid flow rate adjustment valve or the second gas corresponding to the second outdoor unit. An air conditioner adjustment device, wherein the flow rate adjustment valve and the second liquid flow rate adjustment valve are fully closed. According to this configuration, it is possible to reliably prevent the refrigerant from entering and leaving the first outdoor unit or the second outdoor unit that is stopped. For example, the refrigerant of the outdoor unit leaks to the indoor unit and the flow rate is insufficient. It can prevent falling.

  DESCRIPTION OF SYMBOLS 10 ... 1st outdoor unit, 11 ... Electric motor, 12 ... 1st compressor, 15 ... 1st outdoor unit heat exchanger, 14 ... Four-way valve (1st switching valve), 20 ... 2nd outdoor unit, 21 ... Gas Engine, 22 ... second compressor, 24 ... four-way valve (second switching valve), 25 ... second outdoor unit heat exchanger, 29 ... coolant circuit, 30 ... indoor unit, 31 ... indoor unit heat exchanger, 40 ... Air conditioner adjusting device, 40a ... Control part (control means, model information acquisition means, air conditioning load information acquisition means, stop means) 41 ... Gas branch pipe, 41a ... first gas branch part, 41b ... second gas branch part 41c ... Gas collecting part, 42 ... Liquid branch pipe, 42a ... First liquid branching part, 42b ... Second liquid branching part, 42c ... Liquid collecting part, 43 ... First gas flow rate adjusting valve, 44 ... Second gas flow rate Adjustment valve 45 ... first liquid flow rate adjustment valve 46 ... second liquid flow rate adjustment valve 47 ... first pressure control valve Sa, 48 ... second atm sensor, 49 ... first hydraulic pressure sensor, 50 ... second hydraulic pressure sensor.

Claims (6)

A gas branch pipe that connects a ready-made electric heat pump-type first outdoor unit and a ready-made gas heat pump-type second outdoor unit and the indoor unit to flow a gaseous refrigerant;
A liquid branch pipe that connects the first outdoor unit and the second outdoor unit, and the indoor unit to flow a liquid refrigerant;
A first gas flow rate adjusting valve and a second gas flow rate adjusting valve, which are provided in the gas branch pipe and adjust the flow rate of the refrigerant in a gaseous state between the indoor unit and the first outdoor unit and the second outdoor unit; ,
A first liquid flow rate adjustment valve and a second liquid flow rate adjustment valve which are provided in the liquid branch pipe and adjust the flow rate of the refrigerant in a liquid state between the indoor unit and the first outdoor unit and the second outdoor unit; ,
Model information acquisition means for acquiring model information of the first outdoor unit and the second outdoor unit,
Air conditioning load information acquisition means for acquiring air conditioning load information of the indoor unit;
According to the acquired model information and air conditioning load information, the flow rates of the refrigerant respectively supplied from the first outdoor unit and the second outdoor unit to the indoor unit are from the indoor unit to the first outdoor unit and the first outdoor unit. Control means for controlling the opening degree of the first and second gas flow rate adjustment valves and the opening degree of the first and second liquid flow rate adjustment valves so as to match the flow rates of the refrigerant respectively supplied to the two outdoor units. And an air conditioner adjusting device. An electric motor, a first compressor that is driven by the electric motor and sucks refrigerant and compresses and discharges the sucked refrigerant, and is connected to the suction port and the discharge port of the first compressor, respectively, for cooling operation and heating A first switching valve that switches a refrigerant flow path during operation, and a first outdoor unit that is connected to the first switching valve and functions as a refrigerant condenser during cooling operation and as a refrigerant evaporator during heating operation A first outdoor unit having a heat exchanger;
A gas engine, a second compressor that is driven by the gas engine to suck in refrigerant and compresses and discharges the sucked refrigerant, and is connected to a suction port and a discharge port of the second compressor, respectively, for cooling operation and heating A second switching valve that switches the refrigerant flow path during operation, and a second outdoor unit heat that is connected to the second switching valve and functions as a refrigerant condenser during cooling operation and as a refrigerant evaporator during heating operation A second outdoor unit having a exchanger and a coolant circuit that exchanges heat with the exhaust heat of the gas engine and is used to heat the refrigerant during heating operation;
An indoor unit having an indoor unit heat exchanger that functions as a refrigerant evaporator during cooling operation and functions as a refrigerant condenser during heating operation;
In the air conditioner adjusting device for connecting
A gas branch pipe having a first gas branch portion connected to the first switching valve, a second gas branch portion connected to the second switch valve, and a gas collecting portion connected to the indoor unit heat exchanger When,
A first liquid branch connected to the first outdoor unit heat exchanger, a second liquid branch connected to the second outdoor unit heat exchanger, and a liquid assembly connected to the indoor unit heat exchanger A liquid branch pipe having a section;
Provided in the gas branch pipe, during cooling operation, the flow rate of the refrigerant in the gaseous state from the indoor unit heat exchanger is adjusted and supplied to the first compressor via the first switching valve, and during heating operation Is a first gas flow rate adjustment valve that supplies the indoor unit heat exchanger with a gaseous refrigerant discharged from the first compressor through the first switching valve;
Provided in the gas branch pipe, during cooling operation, the flow rate of the refrigerant in the gaseous state from the indoor unit heat exchanger is adjusted and supplied to the second compressor via the second switching valve, and during heating operation Is a second gas flow rate adjustment valve that supplies the refrigerant in the gaseous state via the second switching valve discharged from the second compressor to the indoor unit heat exchanger;
Provided in the liquid branch pipe, supplies a refrigerant in a liquid state from the first outdoor unit heat exchanger to the indoor unit heat exchanger during cooling operation, and supplies liquid from the indoor unit heat exchanger during heating operation. A first liquid flow rate adjustment valve that adjusts the flow rate of refrigerant in a state and supplies the refrigerant to the first outdoor unit heat exchanger;
Provided in the liquid branch pipe, the refrigerant in the liquid state from the second outdoor unit heat exchanger is supplied to the indoor unit heat exchanger during the cooling operation, and the liquid from the indoor unit heat exchanger during the heating operation. A second liquid flow rate adjustment valve that adjusts the flow rate of the refrigerant in a state and supplies the refrigerant to the second outdoor unit heat exchanger;
Model information acquisition means for acquiring model information of the first outdoor unit and the second outdoor unit,
Air conditioning load information acquisition means for acquiring air conditioning load information of the indoor unit;
According to the acquired model information and air conditioning load information, the flow rates of the refrigerant respectively supplied from the first outdoor unit and the second outdoor unit to the indoor unit are from the indoor unit to the first outdoor unit and the first outdoor unit. The opening degree of the first and second gas flow rate regulating valves is controlled during cooling operation so as to match the flow rate of the refrigerant respectively supplied to the two outdoor units, and the first and second liquids are controlled during heating operation. An air conditioner adjusting device comprising control means for controlling the opening degree of the flow rate adjusting valve. In the air conditioner adjusting device according to claim 1 or 2,
An air conditioner adjustment apparatus comprising: a stopping unit that selectively stops the operation of the first outdoor unit and the second outdoor unit based on the acquired model information and air conditioning load information. In the air conditioner adjusting device according to claim 2,
A first atmospheric pressure sensor and a second atmospheric pressure sensor which are disposed in the first gas branching section and the second gas branching section and detect the pressure of the refrigerant flowing through each of the first gas branching section and the second gas branching section;
A first hydraulic pressure sensor and a second hydraulic pressure sensor which are disposed in the first liquid branch portion and the second liquid branch portion and detect the pressure of a refrigerant flowing through each of the first liquid branch portion and the second liquid branch portion;
The control means includes
During the cooling operation, the flow rate of the refrigerant flowing through the first liquid branch portion and the second liquid branch portion corresponding to the refrigerant pressure detected at one and the other of the first hydraulic pressure sensor and the second hydraulic pressure sensor, respectively. Is equal to the flow rate of the refrigerant flowing through the first gas branching portion and the second gas branching portion corresponding to the pressure of the refrigerant detected in one and the other of the first atmospheric pressure sensor and the second atmospheric pressure sensor, respectively. The other and one opening of the first gas flow rate adjustment valve and the second gas flow rate adjustment valve, respectively,
During the heating operation, the flow rate of the refrigerant flowing through the first gas branching portion and the second gas branching portion corresponding to the pressure of the refrigerant detected in one and the other of the first atmospheric pressure sensor and the second atmospheric pressure sensor, respectively, The flow rate of the refrigerant flowing through the first liquid branching portion and the second liquid branching portion corresponds to the refrigerant pressure detected by one and the other of the first hydraulic pressure sensor and the second hydraulic pressure sensor, respectively. The air conditioner adjusting device is characterized in that the other and one opening degree of the first liquid flow rate adjusting valve and the second liquid flow rate adjusting valve are respectively controlled. In the air conditioner adjusting device according to claim 4,
The opening degree of each of the first gas flow rate adjustment valve, the second gas flow rate adjustment valve, the first liquid flow rate adjustment valve and the second liquid flow rate adjustment valve is set to be equal to or greater than a predetermined lower limit opening degree. The air conditioner adjustment device characterized. An electric motor, a first compressor that is driven by the electric motor and sucks refrigerant and compresses and discharges the sucked refrigerant, and is connected to the suction port and the discharge port of the first compressor, respectively, for cooling operation and heating A first switching valve that switches a refrigerant flow path during operation, and a first outdoor unit that is connected to the first switching valve and functions as a refrigerant condenser during cooling operation and as a refrigerant evaporator during heating operation A first outdoor unit having a heat exchanger;
A gas engine, a second compressor that is driven by the gas engine to suck in refrigerant and compresses and discharges the sucked refrigerant, and is connected to a suction port and a discharge port of the second compressor, respectively, for cooling operation and heating A second switching valve that switches the refrigerant flow path during operation, and a second outdoor unit heat that is connected to the second switching valve and functions as a refrigerant condenser during cooling operation and as a refrigerant evaporator during heating operation A second outdoor unit having a exchanger and a coolant circuit that exchanges heat with the exhaust heat of the gas engine and is used to heat the refrigerant during heating operation;
An indoor unit having an indoor unit heat exchanger that functions as a refrigerant evaporator during cooling operation and functions as a refrigerant condenser during heating operation;
An air conditioner adjusting device that connects each of the first outdoor unit and the second outdoor unit to the indoor unit;
The air conditioner adjustment device is:
A gas branch pipe having a first gas branch portion connected to the first switching valve, a second gas branch portion connected to the second switch valve, and a gas collecting portion connected to the indoor unit heat exchanger When,
A first liquid branch connected to the first outdoor unit heat exchanger, a second liquid branch connected to the second outdoor unit heat exchanger, and a liquid assembly connected to the indoor unit heat exchanger A liquid branch pipe having a section;
Provided in the gas branch pipe, during cooling operation, the flow rate of the refrigerant in the gaseous state from the indoor unit heat exchanger is adjusted and supplied to the first compressor via the first switching valve, and during heating operation Is a first gas flow rate adjustment valve that supplies the indoor unit heat exchanger with a gaseous refrigerant discharged from the first compressor through the first switching valve;
Provided in the gas branch pipe, during cooling operation, the flow rate of the refrigerant in the gaseous state from the indoor unit heat exchanger is adjusted and supplied to the second compressor via the second switching valve, and during heating operation Is a second gas flow rate adjustment valve that supplies the refrigerant in the gaseous state via the second switching valve discharged from the second compressor to the indoor unit heat exchanger;
Provided in the liquid branch pipe, supplies a refrigerant in a liquid state from the first outdoor unit heat exchanger to the indoor unit heat exchanger during cooling operation, and supplies liquid from the indoor unit heat exchanger during heating operation. A first liquid flow rate adjustment valve that adjusts the flow rate of refrigerant in a state and supplies the refrigerant to the first outdoor unit heat exchanger;
Provided in the liquid branch pipe, the refrigerant in the liquid state from the second outdoor unit heat exchanger is supplied to the indoor unit heat exchanger during the cooling operation, and the liquid from the indoor unit heat exchanger during the heating operation. A second liquid flow rate adjustment valve that adjusts the flow rate of the refrigerant in a state and supplies the refrigerant to the second outdoor unit heat exchanger;
Model information acquisition means for acquiring model information of the first outdoor unit and the second outdoor unit,
Air conditioning load information acquisition means for acquiring air conditioning load information of the indoor unit;
According to the acquired model information and air conditioning load information, the flow rates of the refrigerant respectively supplied from the first outdoor unit and the second outdoor unit to the indoor unit are from the indoor unit to the first outdoor unit and the first outdoor unit. The opening degree of the first and second gas flow rate adjusting valves is controlled during cooling operation so as to match the flow rate supplied to each of the two outdoor units, and the first and second liquid flow rate adjustments are performed during heating operation. An air conditioner comprising control means for controlling the opening of each valve.

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