JP2019027632A - Air conditioner - Google Patents

Abstract

To shorten a defrosting time, in a hybrid air conditioner.SOLUTION: A GHP outdoor heat exchanger 13 and an EHP outdoor heat exchanger 33 are defrosted simultaneously. Also, in simultaneous defrosting operation, a refrigerant discharged from an EHP compressor 32 is supplied to a sub heat exchanger 19 together with a refrigerant discharged from a GHP compressor 12, and then the refrigerants are heated by the sub heat exchanger 19. Consequently, the refrigerant discharged from the EHP compressor 32 is also heated by the sub heat exchanger 19, thereby accelerating defrosting at the EHP outdoor heat exchanger 33. Accordingly, a defrosting time can be shortened.SELECTED DRAWING: Figure 4

Description

  The present invention relates to an air conditioner.

  During the heating operation of the outdoor unit and the air conditioner including the indoor unit, frost may form on the outdoor heat exchanger of the outdoor unit. In particular, when the outside air temperature is extremely low, the outdoor heat exchanger is likely to be frosted. When the outdoor heat exchanger is frosted, a defrosting operation is performed. Patent Document 1 discloses that, in an air conditioner having a plurality of outdoor units, when an outdoor heat exchanger included in at least one outdoor unit is in a state to be defrosted, defrosting operation is simultaneously started in all the outdoor units. A defrosting method is disclosed.

JP-A-6-313653

(Problems to be solved by the invention)
As a defrosting method for the outdoor heat exchanger, a reverse cycle method is known in which the circulation direction of the refrigerant circulating in the refrigerant circuit is switched from the direction of circulation during the heating operation to the direction of circulation during the cooling operation. According to this method, since the operation state of the air conditioner is in the cooling operation state, cold air is supplied indoors during heating. Therefore, comfort may be impaired. A method of performing defrosting in a heating operation state so as not to impair the comfort as much as possible (hot gas defrosting method) is also known, but the defrosting ability by this method is low, so defrosting is completed in a short time. I can't. Therefore, in order to complete the defrosting in a short time, the defrosting method by the reverse cycle method is more advantageous.

  By the way, the outdoor unit of the air conditioner includes a compressor, a drive source for operating the compressor, and an outdoor heat exchanger through which refrigerant flows in and out by the operation of the compressor. Examples of the drive source include an internal combustion engine such as a gas engine and a motor (electric motor).

  A hybrid type air conditioner that includes both an outdoor unit that uses an internal combustion engine as a drive source and an outdoor unit that uses a motor as a drive source has also been proposed. In such a hybrid type air conditioner, when the outdoor heat exchanger of an outdoor unit using an internal combustion engine as a drive source is defrosted, the heat of the internal combustion engine can be used. For this reason, shortening of defrosting time can be achieved. However, when the outdoor heat exchanger of an outdoor unit using a motor as a drive source is defrosted, the heat of the drive source cannot be used. Therefore, in a hybrid type air conditioner, even if an outdoor heat exchanger provided in an outdoor unit using a motor as a drive source is defrosted by a reverse cycle method, it takes a relatively long time to complete the defrosting. Was.

  The present invention provides a hybrid type air conditioner configured to shorten the defrosting time.

  An air conditioner (1) according to the present invention is a hybrid type air conditioner including a GHP outdoor unit (10), an EHP outdoor unit (30), an indoor unit (40), and a control device (60). is there. The GHP outdoor unit includes an internal combustion engine (11), a GHP compressor (12), a GHP outdoor heat exchanger (13), and a first switching valve (16). The GHP compressor has a first suction port (12a) and a first discharge port (12b), operates by driving the internal combustion engine, sucks refrigerant from the first suction port, and compresses and compresses the sucked refrigerant. Is discharged from the first discharge port. The GHP outdoor heat exchanger is connected to the first suction port of the GHP compressor during the heating operation and is connected to the first discharge port of the GHP compressor during the cooling operation, and exchanges heat between the refrigerant circulating inside and the outside air. The first switching valve has a connection state between the GHP outdoor heat exchanger and the GHP compressor, a heating connection state in which the GHP outdoor heat exchanger is connected to the first suction port, and a cooling connection in which the GHP outdoor heat exchanger is connected to the first discharge port. It can be switched to a state. The EHP outdoor unit includes an electric motor (31), an EHP compressor (32), an EHP outdoor heat exchanger (33), and a second switching valve (36). The EHP compressor has a second suction port (32a) and a second discharge port (32b) and is operated by driving the electric motor to suck refrigerant from the second suction port and compress the compressed refrigerant by compressing the sucked refrigerant. Discharge from the second discharge port. The EHP outdoor heat exchanger is connected to the second suction port of the EHP compressor during the heating operation and is connected to the second discharge port of the EHP compressor during the cooling operation, and exchanges heat between the refrigerant circulating inside and the outside air. The second switching valve has a connection state between the EHP outdoor heat exchanger and the EHP compressor, a heating connection state in which the EHP outdoor heat exchanger is connected to the second suction port, and a cooling connection in which the EHP outdoor heat exchanger is connected to the second discharge port. It can be switched to a state. The indoor unit includes an indoor heat exchanger (41) and an expansion valve (43). The indoor heat exchanger is connected to the first discharge port of the GHP compressor and the second discharge port of the EHP compressor when both the switching state of the first switching valve and the second switching valve are connected during heating. When both the switching state of the first switching valve and the second switching valve are in the cooling state connection state, the refrigerant that is connected to the first suction port of the GHP compressor and the second suction port of the EHP compressor and circulates inside the room air Heat exchange. The expansion valve adjusts the flow rate of the refrigerant flowing through the indoor heat exchanger and expands the refrigerant that has flowed out of the indoor heat exchanger or the refrigerant that flows into the indoor heat exchanger.

  Moreover, the air conditioning apparatus which concerns on this invention is the 1st connection piping (15c, 51, 42a) which connects an indoor heat exchanger and a GHP outdoor heat exchanger, a 1st connection piping (51), and EHP outdoor heat exchange. A second connection pipe (53, 35c) for connecting the heat exchanger and a third connection for connecting the indoor heat exchanger to the first suction port of the GHP compressor when the switching state of the first switching valve is in the cooling state. The fourth connection pipe that connects the pipe (42b, 52, 15f, 15d, 15e) and the third connection pipe and the second suction port of the EHP compressor when the switching state of the second switching valve is the cooling state connection state. (54, 35f, 35d, 35e), a GHP outdoor unit, a sub pipe (15g) connecting the first connection pipe (15c) and the third connection pipe (15d), and a GHP outdoor unit. And when intervened in the sub-pipe To have sub-heat exchanger for heating by the heat obtained by the refrigerant flowing inside the driving of the internal combustion engine (19), the.

  Moreover, the control apparatus with which the air conditioning apparatus which concerns on this invention is equipped controls a 1st switching valve, a 2nd switching valve, and an expansion valve. This control apparatus is comprised so that the simultaneous defrost process which defrosts simultaneously a GHP outdoor heat exchanger and an EHP outdoor heat exchanger can be performed. Then, in the simultaneous defrosting process, the control device switches the connection state of the first switching valve and the second switching valve to the cooling connection state (S31), and the expansion valve that fully closes the expansion valve. A fully-closed process (S33) and a simultaneous defrosting operation process (S35) for operating the GHP compressor and the EHP compressor so that the GHP outdoor heat exchanger and the EHP outdoor heat exchanger are defrosted simultaneously are executed.

  According to the air conditioner according to the present invention, when the control device performs the simultaneous defrosting process, the switching state of the first switching valve and the second switching valve is set to the cooling state connection state. That is, the defrosting process is executed by the reverse cycle method. For this reason, the high-temperature and high-pressure gas refrigerant discharged from the first discharge port of the GHP compressor in the simultaneous defrosting process is supplied to the GHP outdoor heat exchanger, and the GHP outdoor heat exchanger is heated. Thereby, the GHP outdoor heat exchanger is defrosted. In addition, high-temperature and high-pressure gas refrigerant discharged from the second discharge port of the EHP compressor in the simultaneous defrosting process is supplied to the EHP outdoor heat exchanger, and the EHP outdoor heat exchanger is heated. Thereby, the EHP outdoor heat exchanger is defrosted.

  Further, the refrigerant that has flowed out of the GHP outdoor heat exchanger in the simultaneous defrosting process flows into the first connection pipe, and further flows into the sub pipe from the first connection pipe. And a refrigerant | coolant is heated with the heat obtained by the drive of an internal combustion engine in the sub heat exchanger interposed by sub piping. The refrigerant thus heated in the sub heat exchanger flows into the third connection pipe and is sucked into the first suction port of the GHP compressor from the third connection pipe. Thus, the refrigerant | coolant which flows through a GHP outdoor heat exchanger by simultaneous defrost processing is heated by a sub heat exchanger, and a higher temperature refrigerant | coolant can be supplied to a GHP outdoor heat exchanger. Thereby, defrosting of the GHP outdoor heat exchanger is promoted.

  Further, the refrigerant that has flowed out of the EHP outdoor heat exchanger in the simultaneous defrosting process flows into the first connection pipe via the second connection pipe, and further flows into the sub pipe from the first connection pipe. And a refrigerant | coolant is heated with the heat obtained by the drive of an internal combustion engine in the sub heat exchanger interposed by sub piping. Thus, the refrigerant heated in the sub heat exchanger flows into the third connection pipe, flows from the third connection pipe to the fourth connection pipe, and is sucked into the second suction port of the EHP compressor from the fourth connection pipe. The Thus, since the refrigerant flowing through the EHP outdoor heat exchanger in the simultaneous defrosting process is also heated by the sub heat exchanger, a higher temperature refrigerant can be supplied to the EHP outdoor heat exchanger. For this reason, defrosting of the EHP outdoor heat exchanger is promoted.

  Thus, according to the present invention, in the defrosting process of the air conditioner including the GHP outdoor unit and the EHP outdoor unit, not only the defrosting of the GHP outdoor heat exchanger but also the defrosting of the EHP outdoor heat exchanger. Sub heat exchangers can be used. For this reason, the hybrid type air conditioning apparatus which can aim at shortening of a defrost time can be provided.

  An air conditioner according to the present invention is provided in a GHP outdoor unit, and is interposed in a hot gas bypass pipe (15h) that connects a first discharge port and a first suction port, and a hot gas bypass pipe. It is good to provide the hot gas bypass valve (21) which permits or interrupts distribution of the refrigerant in the gas bypass piping. And a control apparatus performs the hot gas bypass valve opening process (S37) which opens a hot gas bypass valve at least when the defrosting of the EHP outdoor heat exchanger is not completed in the simultaneous defrosting process. Good. According to this, when the defrosting of the EHP outdoor heat exchanger is not completed, the hot gas bypass valve is opened, so that a part of the refrigerant discharged from the first discharge port of the GHP compressor is hot gas bypass piping. Through the GHP outdoor heat exchanger and the sub heat exchanger, and is sucked into the first suction port of the GHP compressor. For this reason, the flow rate of the refrigerant supplied from the GHP compressor to the sub heat exchanger during the simultaneous defrosting process is reduced. Therefore, the flow rate of the refrigerant supplied from the EHP compressor to the sub heat exchanger is relatively increased, and as a result, defrosting of the EHP outdoor heat exchanger can be further promoted.

  Moreover, it is good for a control apparatus to perform the hot gas bypass valve closing process (S34) which closes a hot gas bypass valve before execution of simultaneous defrost operation processing by simultaneous defrost processing. According to this, by closing the hot gas bypass valve before the simultaneous defrosting operation process, the refrigerant discharged from the first discharge port of the GHP compressor is efficiently heated by the sub heat exchanger. For this reason, defrosting of the GHP outdoor heat exchanger can be further promoted.

It is a figure which shows schematic structure of the air conditioning apparatus which concerns on this embodiment. It is a flowchart which shows the flow of a defrost start determination processing routine. It is a flowchart which shows the flow of a defrost preparation process routine. It is a flowchart which shows the flow of a simultaneous defrost process routine. It is the schematic of the air conditioning apparatus which concerns on this embodiment by which the flow of the refrigerant | coolant at the time of simultaneous defrost processing was shown. It is a flowchart which shows the flow of an EHP independent defrost process routine. It is a flowchart which shows the flow of GHP independent defrost processing routine.

  Hereinafter, an air conditioner according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a diagram illustrating a schematic configuration of an air-conditioning apparatus according to the present embodiment. The air conditioning apparatus according to the present embodiment is configured to be able to perform a heating operation and a cooling operation. The room is heated by performing the heating operation, and the room is cooled by performing the cooling operation. As shown in FIG. 1, the air conditioning apparatus 1 according to the present embodiment includes a GHP outdoor unit 10, an EHP outdoor unit 30, an indoor unit 40, and a control device 60.

  The GHP outdoor unit 10 includes a gas engine 11 (internal combustion engine), a compressor, a plurality of pipes constituting a refrigerant circuit, and various devices necessary for air conditioning. Each device includes an outdoor heat exchanger, a four-way valve, an outdoor unit fan, an accumulator, a sub heat exchanger, a flow rate adjustment valve, and a hot gas bypass valve. In the present embodiment, “GHP” is given as a prefix to the piping, compressor, outdoor heat exchanger, four-way valve, outdoor unit fan, flow rate adjustment valve, and accumulator provided in the GHP outdoor unit 10. Accordingly, the GHP outdoor unit 10 includes a gas engine 11, a GHP compressor 12, a GHP outdoor heat exchanger 13, a plurality of GHP pipes (15a to 15h), a GHP four-way valve 16, a GHP outdoor unit fan 17, a GHP accumulator 18, a sub heat. The exchanger 19, the GHP flow rate adjustment valve (GHP first flow rate adjustment valve 20 a, GHP second flow rate adjustment valve 20 b), and the hot gas bypass valve 21 are provided.

  The gas engine 11 is driven by using a combustible gas such as propane gas as fuel. The gas engine 11 includes an output shaft 11a. When the gas engine 11 is driven, the output shaft 11a rotates. A GHP compressor 12 is connected to the output shaft 11 a of the gas engine 11 via a clutch 14.

  The GHP compressor 12 operates when the gas engine 11 is driven and the output shaft 11a rotates. The GHP compressor 12 has a first suction port 12a and a first discharge port 12b. When the GHP compressor 12 is operated, a low-pressure gas refrigerant is sucked from the first suction port 12a, and the sucked gas refrigerant is compressed. Then, the compressed high-pressure gas refrigerant is discharged from the first discharge port 12b.

  The first discharge port 12b of the GHP compressor 12 is connected to the GHP four-way valve 16 via the GHP first pipe 15a. The GHP four-way valve 16 corresponds to the first switching valve of the present invention. The GHP four-way valve 16 includes a hollow main body having four ports (a first port 161, a second port 162, a third port 163, and a fourth port 164), and a movable part movable in the main body. . The space in the main body is partitioned so that two specific ports and the other two ports are connected by the movable portion. Moreover, the port to be connected is switched by moving the movable part. The switching state of the GHP four-way valve 16 is controlled by the control device 60. The GHP first pipe 15 a is connected to the first port 161 of the GHP four-way valve 16.

  The second port 162 of the GHP four-way valve 16 is connected to the GHP outdoor heat exchanger 13 via the GHP second pipe 15b. The GHP outdoor heat exchanger 13 includes a first input / output port 13a and a second input / output port 13b. The GHP second pipe 15b is connected to the first input / output port 13a. The GHP outdoor heat exchanger 13 includes a heat exchange tube connecting the first input / output port 13a and the second input / output port 13b, and a heat exchange fin disposed around the heat exchange tube. The GHP outdoor heat exchanger 13 has a function of exchanging heat between the refrigerant flowing in the heat exchange tube and the outside air.

  Further, a GHP outdoor unit fan 17 is installed at a position close to the GHP outdoor heat exchanger 13. A fan motor is attached to the GHP outdoor unit fan 17, and the GHP outdoor unit fan 17 is rotated by driving the fan motor. As the GHP outdoor unit fan 17 rotates, outside air is supplied to the GHP outdoor heat exchanger 13.

  The second input / output port 13b of the GHP outdoor heat exchanger 13 is connected to one end of the GHP third pipe 15c. The other end of the GHP third pipe 15c is connected to a liquid pipe joint 10a provided in the housing of the GHP outdoor unit 10, for example. Further, as can be seen from FIG. 1, the GHP third pipe 15c has a portion branched into two pipes (L1, L2) on the way. One pipe L1 is provided with a GHP second flow rate adjusting valve 20b, and the other pipe L2 is provided with a check valve 20c. During the heating operation, the refrigerant flows through the pipe L1, and during the cooling operation, the refrigerant flows through the pipe l2. The GHP second flow rate adjusting valve 20b interposed in the pipe L1 is configured to be adjustable in opening, and the flow rate of the refrigerant flowing into the GHP outdoor heat exchanger 13 through the pipe L1 (GHP third pipe 15c). Adjust. The check valve 20c allows a refrigerant flow from the GHP outdoor heat exchanger 13 side toward the liquid pipe joint 10a, and blocks a refrigerant flow in the opposite direction.

  The third port 163 of the GHP four-way valve 16 is connected to the GHP accumulator 18 via the GHP fourth pipe 15d. The GHP accumulator 18 supplies a refrigerant from the GHP fourth pipe 15d, and gas-liquid separates the supplied refrigerant. The GHP accumulator 18 is connected to the first suction port 12a of the GHP compressor 12 via the GHP fifth pipe 15e. The gas-phase refrigerant in the GHP accumulator 18 is supplied to the first suction port 12a of the GHP compressor 12 through the GHP fifth pipe 15e.

  The fourth port 164 of the GHP four-way valve 16 is connected to one end of the GHP sixth pipe 15f. The other end of the GHP sixth pipe 15 f is connected to, for example, a gas pipe joint 10 b provided in the housing of the GHP outdoor unit 10.

  Further, the GHP third pipe 15c is connected to the GHP fourth pipe 15d by the GHP seventh pipe 15g, and the part between the liquid pipe joint 10a and the part branched to the pipes L1, L2. The sub heat exchanger 19 is interposed in the GHP seventh pipe 15g. Therefore, the refrigerant flowing through the GHP seventh pipe 15g flows into the sub heat exchanger 19. Cooling water heated by cooling the gas engine 11 is also supplied to the sub heat exchanger 19. Then, in the sub heat exchanger 19, the refrigerant and the cooling water exchange heat. By such heat exchange, the refrigerant flowing in the sub heat exchanger 19 receives heat from the heated cooling water. That is, the refrigerant is heated by the heat (cooling water) obtained by driving the gas engine 11 in the sub heat exchanger 19. Further, the GHP first flow rate adjusting valve 20a is interposed in the GHP seventh pipe 15g. The GHP first flow rate adjusting valve 20a is configured to be able to adjust the opening degree, and adjusts the flow rate of the refrigerant flowing through the GHP seventh pipe 15g, that is, the flow rate of the refrigerant flowing into the sub heat exchanger 19. The GHP seventh pipe 15g corresponds to the sub pipe of the present invention.

  The GHP first pipe 15a and the GHP fourth pipe 15d are connected by a hot gas bypass pipe 15h. The first discharge port 12b and the first suction port 12a of the GHP compressor 12 are connected by the hot gas bypass pipe 15h. A hot gas bypass valve 21 is interposed in the hot gas bypass pipe 15h. The hot gas bypass valve 21 is an on-off valve. The hot gas bypass valve 21 opens or closes to permit or block the refrigerant flow in the hot gas bypass pipe 15h. When the hot gas bypass valve 21 is opened, a part of the refrigerant discharged from the first discharge port 12b of the GHP compressor 12 and flowing out to the GHP first pipe 15a passes through the hot gas bypass pipe 15h. 15d, and further flows into the GHP accumulator 18 from the GHP fourth pipe 15d. The GHP accumulator 18 returns to the first suction port 12a of the GHP compressor 12 through the GHP fifth pipe 15e.

  The EHP outdoor unit 30 includes a motor 31 (an electric motor), a compressor, a plurality of pipes constituting a refrigerant circuit, and various devices necessary for air conditioning. Each device includes an outdoor heat exchanger, a four-way valve, an outdoor unit fan, an accumulator, and a flow rate adjustment valve. In the present embodiment, “EHP” is given as a prefix to piping, compressors, outdoor heat exchangers, four-way valves, outdoor unit fans, and accumulators provided in the EHP outdoor unit. Therefore, the EHP outdoor unit 30 includes a motor 31, an EHP compressor 32, an EHP outdoor heat exchanger 33, a plurality of EHP pipes (35a to 35f), an EHP four-way valve 36, an EHP outdoor unit fan 37, an EHP accumulator 38, and an EHP flow rate adjustment. A valve 39 will be provided.

  The motor 31 is driven by power supplied from a commercial power source C, for example. Note that the generated power of the generator-equipped GHP, the generated power of the generator of the cogeneration system, and the like can be used for driving the motor 31. The motor 31 includes an output shaft 31a. An EHP compressor 32 is connected to the output shaft 31 a of the motor 31.

  The EHP compressor 32 operates by driving the motor 31 and rotating the output shaft 31a. The EHP compressor 32 has a second suction port 32a and a second discharge port 32b. When the EHP compressor 32 is operated, a low-pressure gas refrigerant is sucked from the second suction port 32a, and the sucked gas refrigerant is compressed. Then, the compressed high-pressure gas refrigerant is discharged from the second discharge port 32b.

  The second discharge port 32b of the EHP compressor 32 is connected to the EHP four-way valve 36 via the EHP first pipe 35a. The EHP four-way valve 36 corresponds to the second switching valve of the present invention. The EHP four-way valve 36 includes a hollow main body having four ports (a first port 361, a second port 362, a third port 363, and a fourth port 364), and a movable part movable in the main body. . The space in the main body is partitioned so that two specific ports and the other two ports are connected by the movable portion. Moreover, the port to be connected is switched by moving the movable part. The switching state of the EHP four-way valve 36 is controlled by the control device 60. The EHP first pipe 35 a is connected to the first port 361 of the EHP four-way valve 36.

  The second port 362 of the EHP four-way valve 36 is connected to the EHP outdoor heat exchanger 33 via the EHP second pipe 35b. The EHP outdoor heat exchanger 33 includes a first input / output port 33a and a second input / output port 33b, and an EHP second pipe 35b is connected to the first input / output port 33a. The EHP outdoor heat exchanger 33 includes a heat exchange tube connecting the first input / output port 33a and the second input / output port 33b and a heat exchange fin disposed around the heat exchange tube. The EHP outdoor heat exchanger 33 has a function of exchanging heat between the refrigerant flowing in the heat exchange tube and the outside air.

  Further, an EHP outdoor unit fan 37 is installed at a position close to the EHP outdoor heat exchanger 33. A fan motor is attached to the EHP outdoor unit fan 37, and the EHP outdoor unit fan 37 is rotated by driving the fan motor. As the EHP outdoor unit fan 37 rotates, outside air is supplied to the EHP outdoor heat exchanger 33.

  The second input / output port 33b of the EHP outdoor heat exchanger 33 is connected to one end of the EHP third pipe 35c. The other end of the EHP third pipe 35 c is connected to, for example, a liquid pipe joint 30 a provided in the housing of the EHP outdoor unit 30. Further, as can be seen from FIG. 1, an EHP flow rate adjusting valve 39 is interposed in the EHP third pipe 35c. The EHP flow rate adjustment valve 39 is configured so that the opening degree can be adjusted, and the flow rate of the refrigerant flowing into the EHP outdoor heat exchanger 33 from the EHP third pipe 35c or the EHP outdoor heat exchanger 33 to the EHP third pipe 35c. Adjust the flow rate of the refrigerant flowing into the

  The third port 363 of the EHP four-way valve 36 is connected to the EHP accumulator 38 via the EHP fourth pipe 35d. The EHP accumulator 38 supplies the refrigerant from the EHP fourth pipe 35d and gas-liquid separates the supplied refrigerant. Further, the EHP accumulator 38 is connected to the second suction port 32a of the EHP compressor 32 via the EHP fifth pipe 35e. The gas-phase refrigerant in the EHP accumulator 38 is supplied to the second suction port 32a of the EHP compressor 32 through the EHP fifth pipe 35e.

  The fourth port 364 of the EHP four-way valve 36 is connected to one end of the EHP sixth pipe 35f. The other end of the EHP sixth pipe 35f is connected to, for example, a gas pipe joint 30b provided in the housing of the EHP outdoor unit 30.

  The indoor unit 40 includes one or a plurality of indoor heat exchangers and pipes (indoor side first pipes 42a and indoor side second pipes 42b) provided corresponding to the respective indoor heat exchangers and constituting a refrigerant circuit. And an indoor expansion valve 43 and an indoor unit fan 44 provided corresponding to each indoor heat exchanger. In FIG. 1, three indoor heat exchangers 41A, 41B, and 41C, and respective pipes and devices corresponding thereto are illustrated. The three indoor heat exchangers exemplified are collectively referred to as an indoor heat exchanger 41.

  The indoor heat exchanger 41 includes a first input / output port 41a and a second input / output port 41b. The indoor heat exchanger 41 includes a heat exchange tube connecting the first input / output port 41a and the second input / output port 41b and a heat exchange fin disposed around the heat exchange tube. The indoor heat exchanger 41 has a function of exchanging heat between the refrigerant flowing in the heat exchange tube and room air.

  The first input / output port 41a of the indoor heat exchanger 41 is connected to one end of the indoor first piping 42a. The other end of the indoor first pipe 42a is connected to, for example, a liquid pipe joint 40a provided in the housing of the indoor unit 40. The second input / output port 41b of the indoor heat exchanger 41 is connected to one end of the indoor second piping 42b. The other end of the indoor-side second piping 42b is connected to, for example, a gas pipe joint 40b provided in the housing of the indoor unit 40.

  An indoor expansion valve 43 is interposed in the indoor first piping 42a. The indoor side expansion valve 43 is a flow rate valve whose opening degree can be adjusted. Has a function of expanding the refrigerant.

  An indoor unit fan 44 is installed in the vicinity of the indoor heat exchanger 41. A fan motor is attached to the indoor unit fan 44, and the indoor unit fan 44 is rotated by driving the fan motor. As the indoor unit fan 44 rotates, room air is supplied to the indoor heat exchanger 41.

  Further, as shown in FIG. 1, a liquid pipe joint 10 a provided in the housing of the GHP outdoor unit 10 and a liquid pipe joint 40 a provided in the housing of the indoor unit 40 are connected by a first liquid pipe 51. As described above, the liquid pipe joint 10a of the GHP outdoor unit 10 is connected to the other end of the GHP third pipe 15c, and one end of the third pipe 15c is the second input / output port 13b of the GHP outdoor heat exchanger 13. It is connected to the. The liquid pipe joint 40a of the indoor unit 40 is connected to the other end of the indoor first piping 42a, and the indoor heat exchanger 41 is connected to one end of the indoor first piping 42a. Therefore, the indoor heat exchanger 41 and the GHP outdoor heat exchanger 13 are connected by the GHP third pipe 15c, the first liquid pipe 51, and the indoor first pipe 42a. The GHP third pipe 15c, the first liquid pipe 51, and the indoor first pipe 42a correspond to the first connection pipe of the present invention.

  Further, the gas pipe joint 10 b provided in the housing of the GHP outdoor unit 10 and the gas pipe joint 40 b provided in the housing of the indoor unit 40 are connected by the first gas pipe 52. Here, the gas pipe joint 40b of the indoor unit 40 is connected to the other end of the indoor second pipe 42b, and one end of the indoor second pipe 42b is connected to the indoor heat exchanger 41. The gas pipe joint 10 b of the GHP outdoor unit 10 is connected to the other end of the GHP sixth pipe 15 f, and one end of the GHP sixth pipe 15 f is connected to the fourth port 164 of the GHP four-way valve 16. Further, as will be described later, when the switching state of the GHP four-way valve 16 is the cooling connection state, the fourth port 164 of the GHP four-way valve 16 communicates with the third port 163. The third port 163 of the GHP four-way valve 16 is connected to the GHP accumulator 18 via the GHP fourth pipe 15d, and the GHP accumulator 18 is further connected to the first inlet 12a of the GHP compressor 12 via the GHP fifth pipe 15e. Connected. Accordingly, when the switching state of the GHP four-way valve 16 is the cooling state connection state, the indoor heat exchanger 41 and the first suction port 12a of the GHP compressor 12 are connected to the indoor side second piping 42b, the first gas pipe 52, and the GHP first. The six pipes 15f, the GHP fourth pipe 15d, and the GHP fifth pipe 15e are connected. The indoor second pipe 42b, the first gas pipe 52, the GHP sixth pipe 15f, the GHP fourth pipe 15d, and the GHP fifth pipe 15e correspond to the third connection pipe of the present invention.

  The first liquid pipe 51 communicates with one end of the second liquid pipe 53. The other end of the second liquid pipe 53 is connected to a liquid pipe joint 30 a provided in the housing of the EHP outdoor unit 30. The liquid pipe joint 30a of the EHP outdoor unit 30 is connected to the other end of the EHP third pipe 35c, and one end of the EHP third pipe 35c is connected to the second input / output port 33b of the EHP outdoor heat exchanger 33. . Therefore, the first liquid pipe 51 (first connection pipe) and the EHP outdoor heat exchanger 33 are connected by the second liquid pipe 53 and the EHP third pipe 35c. The second liquid pipe 53 and the EHP third pipe 35c correspond to the second connection pipe of the present invention.

  The first gas pipe 52 communicates with one end of the second gas pipe 54. The other end of the second gas pipe 54 is connected to a gas pipe joint 30 b provided in the housing of the EHP outdoor unit 30. The gas pipe joint 30 b of the EHP outdoor unit 30 is connected to the other end of the EHP sixth pipe 35 f, and one end of the EHP sixth pipe 35 f is connected to the fourth port 364 of the EHP four-way valve 36. Further, as will be described later, when the switching state of the EHP four-way valve 36 is the cooling connection state, the fourth port 364 of the EHP four-way valve 16 communicates with the third port 363. The third port 363 of the EHP four-way valve 36 is connected to the EHP accumulator 38 via the EHP fourth pipe 35d, and the EHP accumulator 38 is further connected to the second suction port 32a of the EHP compressor 32 via the EHP fifth pipe 35e. Connected. Accordingly, when the switching state of the EHP four-way valve 36 is the cooling connection state, the first gas pipe 52 (third connection pipe) and the second suction port 32a of the EHP compressor 32 are connected to the second gas pipe 54, the EHP sixth. The pipe 35f, the EHP fourth pipe 35d, and the EHP fifth pipe 35e are connected. The second gas pipe 54, the EHP sixth pipe 35f, the EHP fourth pipe 35d, and the EHP fifth pipe 35e correspond to the fourth connection pipe of the present invention.

  The control device 60 mainly includes a microcomputer including a CPU, a ROM, and a RAM, and controls the operation of the air conditioner 1. For example, the control device 60 switches the GHP four-way valve 16 and the EHP four-way valve 36 according to the operating state of the air conditioner 1, the rotation speed of the gas engine 11, the rotation speed of the motor 31, and the indoor expansion valve 43. The opening degree, the opening degree of each flow regulating valve (20a, 20b, 39), the open / closed state of the hot gas bypass valve 21, the rotational speed of each fan, and the like are controlled.

  Although not shown in FIG. 1, sensors are provided at various locations of the GHP outdoor unit 10, the EHP outdoor unit 30, and the indoor unit 40, and detection signals from these sensors are input to the control device 60. The control device 60 controls the operation of the air conditioner 1 based on signals input from various sensors. As various sensors, a rotation speed detection sensor that detects the rotation speed of the gas engine 11 and the motor 31, a discharge temperature sensor that detects the temperature of the refrigerant discharged from the GHP compressor 12 and the EHP compressor 32, the GHP compressor 12 and the EHP compressor 32, and the like. An intake temperature sensor for detecting the temperature of the refrigerant sucked in, a pressure sensor for detecting the pressure of the refrigerant sucked into the GHP compressor 12 and the EHP compressor 32, and an inflow and outflow into the GHP outdoor heat exchanger 13 and the EHP outdoor heat exchanger 33. A temperature sensor for detecting the temperature of the refrigerant to be performed, a temperature sensor for detecting the temperature of the refrigerant circulating in the GHP outdoor heat exchanger 13 and the EHP outdoor heat exchanger 33, a rotational speed detection sensor for detecting the rotational speed of various fans, Openings of the indoor expansion valve 43 and the flow rate adjustment valves (20a, 20b, 39) Opening detection sensor for detecting a temperature sensor for detecting the outside air temperature, it can be exemplified such as this shall not apply.

  Next, the operation | movement at the time of the heating operation of the air conditioning apparatus 1 of the said structure and the air_conditionaing | cooling operation is demonstrated. First, the operation during heating operation will be described. During the heating operation, the control device 60 controls each of the four-way valves so that the switching state of the GHP four-way valve 16 and the EHP four-way valve 36 becomes the connection state during heating. Here, the GHP four-way valve 16 and the EHP four-way valve 36 are configured so that the switching state can be switched between a heating connection state and a cooling connection state described later. The connection state during heating means that the first ports (161, 361) and the fourth ports (164, 364) of both the four-way valves (16, 36) communicate with each other and the second ports (162, 362) and the third port ( 163, 363) communicate with each other. Accordingly, the first pipe connected to the first port (161, 361) of the four-way valve (16, 36) during the heating operation, that is, when the switching state of both the four-way valves (16, 36) is the connection state during heating. (15a, 35a) is connected to the sixth pipe (15f, 35f) connected to the fourth port (164, 364) and connected to the second port (162, 362) of the four-way valve (16, 36). The second pipe (15b, 35b) is connected to the fourth pipe (15d, 35d) connected to the third port (163, 363).

  As can be seen from the description below, when the switching state of the GHP four-way valve 16 is the heating connection state, the GHP outdoor heat exchanger 13 is connected to the first suction port 12a of the GHP compressor 12, and the GHP four-way valve 16 When the switching state is the connection state during cooling, the GHP outdoor heat exchanger 13 is connected to the first discharge port 12b of the GHP compressor 12. Therefore, the GHP four-way valve 16 changes the connection state between the GHP outdoor heat exchanger 13 and the GHP compressor 12, and the connection state during heating when the GHP outdoor heat exchanger 13 is connected to the first inlet 12 a of the GHP compressor 12. It can be said that it is configured to be switchable to the cooling-time connection state connected to the first discharge port 12b of the compressor 12. Similarly, when the switching state of the EHP four-way valve 36 is a connection state during heating, the EHP outdoor heat exchanger 33 is connected to the second inlet 32a of the EHP compressor 32, and the switching state of the EHP four-way valve 36 is connected during cooling. When in the state, the EHP outdoor heat exchanger 33 is connected to the second discharge port 32 b of the EHP compressor 32. Therefore, the EHP four-way valve 36 has a connection state between the EHP outdoor heat exchanger 33 and the EHP compressor 32, and a connection state during heating in which the EHP outdoor heat exchanger 33 is connected to the second inlet 32a of the EHP compressor 32. It can be said that it is configured to be switchable to the cooling state connection state connected to the second discharge port 32b of the compressor 32.

  Further, during the heating operation, the gas engine 11 is driven in a state where the switching state of the GHP four-way valve 16 is set to the connection state during heating. Then, the GHP compressor 12 is operated to suck the low-pressure gas refrigerant in the GHP fifth pipe 15e from the first suction port 12a and compress the sucked low-pressure gas refrigerant to generate a high-temperature high-pressure gas refrigerant. Then, the generated high-temperature and high-pressure gas refrigerant is discharged from the first discharge port 12b. The high-temperature and high-pressure gas refrigerant discharged from the first discharge port 12b flows through the GHP first pipe 15a and flows into the GHP four-way valve 16.

  During the heating operation, the GHP first pipe 15a is connected to the GHP sixth pipe 15f by the GHP four-way valve 16, so the high-temperature and high-pressure gas refrigerant flowing from the GHP first pipe 15a to the GHP four-way valve 16 is the GHP four-way valve 16. Flows into the GHP sixth pipe 15f. The high-temperature high-pressure gas refrigerant that has flowed into the GHP sixth pipe 15f further passes through the gas pipe joint 10b of the GHP outdoor unit 10, the first gas pipe 52, the gas pipe joint 40b of the indoor unit 40, and the indoor second pipe 42b in this order. Flowing. And it flows in into the indoor heat exchanger 41 connected to the indoor side 2nd piping 42b from the 2nd input / output port 41b.

  The high-temperature and high-pressure gas refrigerant that has flowed into the indoor heat exchanger 41 exchanges heat with the indoor air while flowing through the heat exchange tube of the indoor heat exchanger 41, and discharges heat to the indoor air to condense. That is, the indoor heat exchanger 41 functions as a condenser during heating operation. At this time, the room air is warmed by the heat discharged from the high-temperature and high-pressure gas refrigerant, and the room is heated.

  The refrigerant that is exhausted and condensed in the indoor air by the indoor heat exchanger 41 is partially liquefied and flows out from the first input / output port 41a of the indoor heat exchanger 41 to the indoor first piping 42a. And it is pressure-reduced so that it may evaporate easily by expanding with the indoor side expansion valve 43 interposed in the middle of the indoor side 1st piping 42a. The refrigerant expanded by the indoor side expansion valve 43 is further supplied from the indoor side first pipe 42a to the liquid pipe joint 40a of the indoor unit 40, the first liquid pipe 51, the liquid pipe joint 10a of the GHP outdoor unit 10, and the GHP third pipe. It flows into the GHP outdoor heat exchanger 13 from the second input / output port 13b via 15c, the pipe L1 and the GHP second flow rate adjusting valve 20b. The refrigerant that has flowed into the GHP outdoor heat exchanger 13 exchanges heat with the outside air while flowing through the heat exchange tube of the GHP outdoor heat exchanger 13, and takes the heat of the outside air to evaporate. That is, the GHP outdoor heat exchanger 13 functions as an evaporator during heating.

  The refrigerant that has evaporated the heat of the outside air in the GHP outdoor heat exchanger 13 is partially vaporized and flows out from the first input / output port 13a of the GHP outdoor heat exchanger 13 to the GHP second pipe 15b. Then, the GHP four-way valve 16 enters the GHP second pipe 15b. Since the GHP second pipe 15b is connected to the GHP fourth pipe 15d by the GHP four-way valve 16 during the heating operation, the refrigerant flowing into the GHP four-way valve 16 from the GHP second pipe 15b is transferred from the GHP four-way valve 16 to the GHP fourth pipe. It flows into the pipe 15d and is further supplied to the GHP accumulator 18. In the GHP accumulator 18, the supplied refrigerant is gas-liquid separated. Only the low-temperature and low-pressure gas refrigerant flows out from the GHP accumulator 18 to the GHP fifth pipe 15e. The refrigerant that has flowed out of the GHP accumulator 18 to the GHP fifth pipe 15 e returns to the first suction port 12 a of the GHP compressor 12. As can be seen from the flow of the refrigerant, during the heating operation in which the switching state of the GHP four-way valve 16 is the connection state during heating, the GHP outdoor heat exchanger 13 includes the GHP second pipe 15b, the GHP fourth pipe 15d, and the GHP first. It is connected to the first inlet 12a of the GHP compressor 12 via the five pipes 15e.

  Further, during heating operation, the opening degree of the GHP first flow rate adjustment valve 20a is controlled as necessary. When the GHP first flow rate adjustment valve 20a is open, a part of the refrigerant flowing into the GHP third pipe 15c through the indoor heat exchanger 41 and the indoor side expansion valve 43 flows into the GHP seventh pipe 15g. The refrigerant that has flowed into the GHP seventh pipe 15 g is introduced into the sub heat exchanger 19. In the sub heat exchanger 19, the refrigerant exchanges heat with the cooling water, whereby the refrigerant is heated. The refrigerant heated by the sub heat exchanger 19 flows out from the GHP seventh pipe 15g to the GHP fourth pipe 15d, and then supplied to the GHP accumulator 18.

  Further, during the heating operation, the motor 31 is driven in a state where the switching state of the EHP four-way valve 36 is set to the connection state during heating. Then, the EHP compressor 32 is operated to suck the low-pressure gas refrigerant in the EHP fifth pipe 35e from the second suction port 32a and compress the sucked low-pressure gas refrigerant to generate a high-temperature and high-pressure gas refrigerant. And the produced | generated high temperature / high pressure gas refrigerant | coolant is discharged from the 2nd discharge port 32b. The high-temperature and high-pressure gas refrigerant discharged from the second discharge port 32b flows through the EHP first pipe 35a and flows into the EHP four-way valve 36.

  During the heating operation, since the EHP first pipe 35a is connected to the EHP sixth pipe 35f by the EHP four-way valve 36, the high-temperature and high-pressure gas refrigerant flowing into the EHP four-way valve 36 from the EHP first pipe 35a is the EHP four-way valve 36. Flows into the EHP sixth pipe 35f. The high-temperature high-pressure gas refrigerant that has flowed into the EHP sixth pipe 35f further includes the gas pipe joint 30b of the EHP outdoor unit 30, the second gas pipe 54, the first gas pipe 52, the gas pipe joint 40b of the indoor unit 40, It flows through the two pipes 42b in this order. And it flows in into the indoor heat exchanger 41 connected to the indoor side 2nd piping 42b from the 2nd input / output port 41b.

  The high-temperature and high-pressure gas refrigerant that has flowed into the indoor heat exchanger 41 exchanges heat with the indoor air while flowing through the heat exchange tube of the indoor heat exchanger 41, and discharges heat to the indoor air to condense. At this time, the room air is warmed by the heat discharged from the high-temperature and high-pressure gas refrigerant, and the room is heated.

  The refrigerant that is exhausted and condensed in the indoor air by the indoor heat exchanger 41 is partially liquefied and flows out from the first input / output port 41a of the indoor heat exchanger 41 to the indoor first piping 42a. And it is pressure-reduced so that it may evaporate easily by expanding with the indoor side expansion valve 43 interposed in the middle of the indoor side 1st piping 42a. The refrigerant expanded by the indoor expansion valve 43 further includes the liquid pipe joint 40a, the first liquid pipe 51, the second liquid pipe 53, the liquid pipe joint 30a of the EHP outdoor unit 30, and the EHP third pipe 35c. And flows into the EHP outdoor heat exchanger 33 from the second input / output port 33b via the EHP flow rate adjustment valve 39. The refrigerant flowing into the EHP outdoor heat exchanger 33 exchanges heat with the outside air while flowing through the heat exchange tube in the EHP outdoor heat exchanger 33, and evaporates by taking the heat of the outside air. That is, the EHP outdoor heat exchanger 33 functions as an evaporator during heating.

  A part of the refrigerant evaporated by removing heat from the outside air in the EHP outdoor heat exchanger 33 is vaporized and flows out from the first input / output port 33a of the EHP outdoor heat exchanger 33 to the EHP second pipe 35b. And it enters into the EHP four-way valve 36 from the EHP second pipe 35b. Since the EHP second pipe 35b is connected to the EHP fourth pipe 35d by the EHP four-way valve 36 during the heating operation, the refrigerant flowing into the EHP four-way valve 36 from the EHP second pipe 35b is transferred from the EHP four-way valve 36 to the EHP fourth pipe. It flows into the pipe 35d and is further supplied to the EHP accumulator 38. In the EHP accumulator 38, the supplied refrigerant is gas-liquid separated. Only the low-temperature and low-pressure gas refrigerant flows out from the EHP accumulator 38 to the EHP fifth pipe 35e. The refrigerant that has flowed out of the EHP accumulator 38 to the EHP fifth pipe 35 e returns to the second suction port 32 a of the EHP compressor 32. As can be seen from the flow of the refrigerant, during the heating operation in which the switching state of the EHP four-way valve 36 is the connection state during heating, the EHP outdoor heat exchanger 33 includes the EHP second pipe 35b, the EHP fourth pipe 35d, and the EHP first It is connected to the second suction port 32a of the EHP compressor 32 via the five pipes 35e. In FIG. 1, the flow of the refrigerant during the heating operation is indicated by a solid line arrow.

  Next, the cooling operation will be described. During the cooling operation, the control device 60 controls each of the four-way valves so that the switching state of the GHP four-way valve 16 and the EHP four-way valve 36 becomes a connection state during cooling. Here, in the cooling state, the first ports (161, 361) and the second ports (162, 362) of the four-way valves (16, 36) communicate with each other and the third ports (163, 363) and the second ports (163, 363) communicate with each other. This is a switching state in which the four ports (164, 364) communicate. Therefore, the first piping connected to the first port (161, 361) of the four-way valve (16, 36) during the cooling operation, that is, when the switching state of both the four-way valves (16, 36) is the connection state during cooling. (15a, 35a) is connected to the second pipe (15b, 35b) connected to the second port (162, 362), and the fourth pipe (15d, 35d) is connected to the third port (163, 363). Is connected to the sixth pipe (15f, 35f) connected to the fourth port (164, 364).

  Further, during the cooling operation, the gas engine 11 is driven in a state where the switching state of the GHP four-way valve 16 is set to the connection state during cooling. Then, the GHP compressor 12 is operated to suck the low-pressure gas refrigerant in the GHP fifth pipe 15e from the first suction port 12a and compress the sucked low-pressure gas refrigerant to generate a high-temperature high-pressure gas refrigerant. Then, the generated high-temperature and high-pressure gas refrigerant is discharged from the first discharge port 12b. The high-temperature and high-pressure gas refrigerant discharged from the first discharge port 12b flows through the GHP first pipe 15a and flows into the GHP four-way valve 16.

  During the cooling operation, since the GHP first pipe 15a is connected to the GHP second pipe 15b by the GHP four-way valve 16, the high-temperature and high-pressure gas refrigerant flowing into the GHP four-way valve 16 from the GHP first pipe 15a is the GHP four-way valve 16. Flows into the GHP second pipe 15b. The high-temperature and high-pressure gas refrigerant that has flowed into the GHP second pipe 15b flows into the GHP outdoor heat exchanger 13 connected to the GHP second pipe 15b from the first input / output port 13a. The refrigerant that has flowed into the GHP outdoor heat exchanger 13 exchanges heat with the outside air while flowing through the heat exchange tube of the GHP outdoor heat exchanger 13, and then condenses by discharging heat to the outside air. That is, the GHP outdoor heat exchanger 13 functions as a condenser during cooling. As can be seen from the refrigerant flow described above, during the cooling operation in which the switching state of the GHP four-way valve 16 is in the cooling connection state, the GHP outdoor heat exchanger 13 connects the GHP second pipe 15b and the GHP first pipe 15a. To the first discharge port 12 b of the GHP compressor 12.

  The refrigerant that is condensed by discharging heat to the outside air in the GHP outdoor heat exchanger 13 is partially liquefied and flows out from the second input / output port 13b of the GHP outdoor heat exchanger 13 to the GHP third pipe 15c. The refrigerant flowing into the GHP third pipe 15c passes through the pipe L2, the check valve 20c, the liquid pipe joint 10a of the GHP outdoor unit 10, the first liquid pipe 51, and the liquid pipe joint 40a of the indoor unit 40 to the indoor side. The pressure reaches the first pipe 42a, and the pressure is reduced so that the first pipe 42a is easily evaporated by being expanded by the indoor expansion valve 43 interposed in the middle of the indoor first pipe 42a. The refrigerant expanded by the indoor expansion valve 43 flows into the indoor heat exchanger 41 from the first input / output port 41a. The refrigerant that has flowed into the indoor heat exchanger 41 exchanges heat with the indoor air while flowing through the heat exchange tube of the indoor heat exchanger 41, and evaporates by taking away the heat of the indoor air. That is, the indoor heat exchanger 41 functions as an evaporator during cooling. At this time, the heat is taken away by the refrigerant, thereby cooling the indoor air and cooling the room.

  The refrigerant that has evaporated the heat of the indoor air in the indoor heat exchanger 41 flows out from the second input / output port 41b of the indoor heat exchanger 41 to the indoor second piping 42b. The refrigerant that has flowed into the indoor second pipe 42b passes through the gas pipe joint 40b of the indoor unit 40, the first gas pipe 52, the gas pipe joint 10b of the GHP outdoor unit 10, and the GHP sixth pipe 15f. Enter 16. Since the GHP sixth pipe 15f is connected to the GHP fourth pipe 15d by the GHP four-way valve 16 during the cooling operation, the refrigerant flowing into the GHP four-way valve 16 from the GHP sixth pipe 15f is transferred from the GHP four-way valve 16 to the GHP fourth pipe. It flows into the pipe 15d and is further supplied to the GHP accumulator 18. In the GHP accumulator 18, the supplied refrigerant is gas-liquid separated. Only the low-temperature and low-pressure gas refrigerant flows out from the GHP accumulator 18 to the GHP fifth pipe 15e. The refrigerant that has flowed out of the GHP accumulator 18 to the GHP fifth pipe 15 e returns to the first suction port 12 a of the GHP compressor 12. As can be seen from the flow of the refrigerant, when the cooling operation is performed, that is, when the switching state of the GHP four-way valve 16 is the cooling connection state, the indoor heat exchanger 41 is connected to the third connection pipe (the indoor second pipe 42b, The first gas pipe 52, the GHP sixth pipe 15f, the GHP fourth pipe 15d, and the GHP fifth pipe 15e) are connected to the first suction port 12a of the GHP compressor 12.

  Further, during the cooling operation, the motor 31 is driven in a state where the switching state of the EHP four-way valve 36 is set to the connection state during cooling. Then, the EHP compressor 32 is operated to suck the low-pressure gas refrigerant in the EHP fifth pipe 35e from the second suction port 32a and compress the sucked low-pressure gas refrigerant to generate a high-temperature and high-pressure gas refrigerant. And the produced | generated high temperature / high pressure gas refrigerant | coolant is discharged from the 2nd discharge port 32b. The high-temperature and high-pressure gas refrigerant discharged from the second discharge port 32b flows through the EHP first pipe 35a and flows into the EHP four-way valve 36.

  During the cooling operation, since the EHP first pipe 35a is connected to the EHP second pipe 35b by the EHP four-way valve 36, the high-temperature and high-pressure gas refrigerant flowing into the EHP four-way valve 36 from the EHP first pipe 35a is the EHP four-way valve 36. To the EHP second pipe 35b. The high-temperature and high-pressure gas refrigerant that has flowed into the EHP second pipe 35b flows into the EHP outdoor heat exchanger 33 connected to the EHP second pipe 35b from its first input / output port 33a. The refrigerant that has flowed into the EHP outdoor heat exchanger 33 exchanges heat with the outside air while flowing through the heat exchange tube of the EHP outdoor heat exchanger 33, and heat is discharged to the outside air to condense. That is, the EHP outdoor heat exchanger 33 functions as a condenser during cooling. As can be seen from the refrigerant flow described above, during the cooling operation in which the switching state of the EHP four-way valve 36 is the cooling connection state, the EHP outdoor heat exchanger 33 connects the EHP second pipe 35b and the EHP first pipe 35a. Through the second discharge port 32 b of the EHP compressor 32.

  The refrigerant that is condensed by discharging heat to the outside air in the EHP outdoor heat exchanger 33 is partially liquefied and flows out from the second input / output port 33b of the EHP outdoor heat exchanger 33 to the EHP third pipe 35c. The refrigerant flowing into the EHP third pipe 35c passes through the EHP flow rate adjusting valve 39, the liquid pipe joint 30a of the EHP outdoor unit 30, the second liquid pipe 53, the first liquid pipe 51, and the liquid pipe joint 40a of the indoor unit 40. Thus, the pressure reaches the indoor first piping 42a, and the pressure is reduced so as to easily evaporate by expansion by the indoor expansion valve 43 interposed in the middle of the indoor first piping 42a. The refrigerant expanded by the indoor expansion valve 43 flows into the indoor heat exchanger 41 from the first input / output port 41a. The refrigerant that has flowed into the indoor heat exchanger 41 exchanges heat with the indoor air while flowing through the heat exchange tube of the indoor heat exchanger 41, and evaporates by taking away the heat of the indoor air. At this time, the heat is taken away by the refrigerant, thereby cooling the indoor air and cooling the room.

  The refrigerant that has evaporated the heat of the indoor air in the indoor heat exchanger 41 flows out from the second input / output port 41b of the indoor heat exchanger 41 to the indoor second piping 42b. The refrigerant that has flowed out into the indoor second pipe 42b passes through the gas pipe joint 40b, the first gas pipe 52, the second gas pipe 54, the gas pipe joint 30b of the EHP outdoor unit 30, and the EHP sixth pipe 35f. Then, the EHP four-way valve 36 is entered. Since the EHP sixth pipe 35f is connected to the EHP fourth pipe 35d by the EHP four-way valve 36 during the cooling operation, the refrigerant flowing into the EHP four-way valve 36 from the EHP sixth pipe 35f is transferred from the EHP four-way valve 36 to the EHP fourth pipe 36f. It flows into the pipe 35d and is further supplied to the EHP accumulator 38. In the EHP accumulator 38, the supplied refrigerant is gas-liquid separated. Only the low-temperature and low-pressure gas refrigerant flows out from the EHP accumulator 38 to the EHP fifth pipe 35e. The refrigerant that has flowed out of the EHP accumulator 38 to the EHP fifth pipe 35 e returns to the second suction port 32 a of the EHP compressor 32. As can be seen from the flow of the refrigerant, during the cooling operation, that is, when the switching state of the EHP four-way valve 36 is the cooling connection state, the indoor heat exchanger 41 includes the indoor second pipe 42b and the first gas pipe 52. The second gas pipe 54, the EHP sixth pipe 35f, the EHP fourth pipe 35d, and the EHP fifth pipe 35e are connected to the second suction port 32a of the EHP compressor 32. In FIG. 1, the flow of the refrigerant during the cooling operation is indicated by a dashed arrow.

  During the heating operation and the cooling operation of the air conditioner 1 as described above, the control device 60 controls the GHP outdoor unit 10 and the EHP outdoor unit 30 according to the air conditioning load required from the indoor unit 40. For example, when the required air conditioning load is large, the control device 60 controls the GHP outdoor unit 10 and the EHP outdoor unit 30 so that the refrigerant flows through both the GHP outdoor heat exchanger 13 and the EHP outdoor heat exchanger 33. be able to. Further, when the required air conditioning load is small, the control device 60 sets the GHP outdoor unit 10 and the EHP outdoor unit 30 so that the refrigerant flows through either the GHP outdoor heat exchanger 13 or the EHP outdoor heat exchanger 13. Can be controlled.

  In addition, the control device 60 can control the outdoor unit (10, 30) and / or the indoor unit so that the heat exchange amount of the indoor heat exchanger 41 during operation becomes an amount commensurate with the air conditioning load during the heating operation and the cooling operation. The machine 40 is controlled. For example, the control device 60 includes the rotation speed of the gas engine 11 of the GHP outdoor unit 10, the rotation speed of the motor 31 of the EHP outdoor unit 30, the opening degree of the indoor expansion valve 43 of the indoor unit 40, and the rotation speed of the indoor unit fan 44. , Etc. are controlled to control the heat exchange amount of the indoor heat exchanger 41 during operation.

  Further, the hot gas bypass valve 21 is normally closed during the heating operation and the cooling operation described above. The hot gas bypass valve 21 is opened as necessary. For example, the hot gas bypass valve 21 is opened when the pressure of the refrigerant sucked into the GHP compressor 12 becomes low and there is a possibility that the air conditioning operation is stopped due to a low pressure abnormality. Thereby, the high-pressure gas refrigerant is sucked into the GHP compressor 12, and as a result, the low-pressure abnormality is avoided.

  By the way, at the time of heating operation, especially at the time of heating operation when the outside air temperature is very low, the temperature of the refrigerant discharged from the outdoor heat exchanger (refrigerant evaporation temperature) may decrease below freezing point and below the dew point. In this case, frost is formed on the heat exchange fins provided in the outdoor heat exchanger. When the heating operation is continued with frost on the heat exchange fins, frost grows and the heat exchange fins are covered with frost. In addition, the ventilation area decreases due to the growth of frost. For this reason, the heat exchange performance in the outdoor heat exchanger is impaired.

  Therefore, when the outdoor heat exchanger is frosted during the heating operation, the defrosting operation is performed. Below, the defrost operation which the air conditioning apparatus 1 which concerns on this embodiment implements is demonstrated.

  In this embodiment, the control apparatus 60 performs a defrost start determination process at the time of heating operation. FIG. 2 is a flowchart showing a flow of a defrosting start determination processing routine executed by the control device 60. When the routine shown in FIG. 2 is started, first, the control device 60 determines whether or not the defrosting start condition is satisfied in step S11 of FIG. 2 (hereinafter, step is abbreviated as S) and S11. In this case, for example, the temperature of the refrigerant flowing into the GHP outdoor heat exchanger 13 during the heating operation (that is, the temperature of the refrigerant flowing through the GHP third pipe 15c) is equal to or lower than the temperature that is predetermined as the temperature at which defrosting needs to be started. (Condition A), the temperature of the refrigerant flowing out of the GHP outdoor heat exchanger 13 during the heating operation (that is, the temperature of the refrigerant flowing through the GHP second pipe 15b) is determined in advance as the temperature at which defrosting needs to be started. The temperature of the refrigerant flowing through the GHP outdoor heat exchanger 13 during the heating operation is equal to or lower than a temperature that is predetermined as a temperature at which defrosting needs to be started (C condition). ), The temperature of the refrigerant flowing into the EHP outdoor heat exchanger 33 during the heating operation (that is, the temperature of the refrigerant flowing through the EHP third pipe 35c) is preliminarily determined as a temperature at which defrosting needs to be started. It is necessary to start defrosting when the temperature is lower than a predetermined temperature (D condition), and the temperature of the refrigerant flowing out of the EHP outdoor heat exchanger 33 during the heating operation (that is, the temperature of the refrigerant flowing through the EHP second pipe 35b). The temperature is equal to or lower than a predetermined temperature (E condition), and the temperature of the refrigerant circulating in the EHP outdoor heat exchanger 33 during the heating operation is equal to or lower than a temperature that is predetermined as a temperature at which defrosting needs to be started. It can be determined that the defrosting start condition is satisfied when at least one of the certain conditions (F condition) is satisfied.

  When it is determined in S11 that the defrosting start condition is not satisfied (S11: No), the control device 60 proceeds to S13, sets the defrosting start flag to OFF, and then ends this routine. To do. On the other hand, when it is determined in S11 that the defrosting start condition is satisfied (S11: Yes), the control device 60 proceeds to S12, sets the defrosting start flag to ON, and then ends this routine. To do.

  When the defrost start flag is set to OFF in the defrost start determination process, the heating operation is continued without executing the defrost operation. On the other hand, when the defrost start flag is set to ON in the defrost start determination process, the defrost operation is performed. In this case, the control device 60 first executes a defrost preparation process. FIG. 3 is a flowchart showing a flow of a defrost preparation processing routine executed by the control device 60. When this routine is started, the control device 60 first determines whether or not there is a compressor that is not operating (non-operating compressor) among the GHP compressor 12 and the EHP compressor 32 in S21 of FIG. When there is no non-operation compressor (S21: No), control device 60 ends this routine. On the other hand, when there exists a non-operation compressor (S21: Yes), the control apparatus 60 advances a process to S22, and outputs the operation command signal for operating a non-operation compressor.

  Next, in S23, control device 60 determines whether or not all the compressors (GHP compressor 12 and EHP compressor 32) are operating. Even when the operation command signal for operating the non-operating compressor is output in the defrost preparation process according to the present embodiment, the non-operating compressor is caused by other control or due to an abnormality or failure of the outdoor unit. May not work. In such a case, even if the operation command signal is output in S22, the non-operating compressor does not operate. When it is determined in S23 that all the compressors are operating (S23: Yes), that is, when all the outdoor units are operating and performing the heating operation, the control device 60 performs the process in S24. Go ahead and set the simultaneous defrost flag to ON. Thereafter, the control device 60 ends this routine. On the other hand, when any of the compressors is not operating (S23: No), the control device 60 proceeds to S25 and sets the single defrost flag to ON. Thereafter, the control device 60 ends this routine.

  When the control device 60 executes the defrost preparation process shown in FIG. 3, all the operable compressors are operated before the defrost operation is performed. Therefore, when it becomes necessary to defrost even one of all the outdoor heat exchangers, it includes an outdoor unit that is stopped and an outdoor unit that includes an outdoor heat exchanger that does not require defrosting. All the outdoor units are put into the heating operation state except when the outdoor unit cannot be operated.

  When the simultaneous defrost flag is set to ON in the defrost preparation process, the control device 60 executes the simultaneous defrost process. FIG. 4 is a flowchart showing the flow of the simultaneous defrosting process routine executed by the control device 60. When the routine shown in FIG. 4 is started, the control device 60 first executes switching processing of the GHP four-way valve 16 and the EHP four-way valve 36 in S31 of FIG. By executing this process, the switching state of the GHP four-way valve 16 is changed from the connection state during heating to the connection state during cooling, and the switching state of the EHP four-way valve 36 is changed from the connection state during heating to the connection state during cooling. . The process of S31 corresponds to the connection state switching process of the present invention.

  Subsequently, the control device 60 outputs a stop signal to the fan motor attached to all the indoor unit fans 44. Thereby, all the indoor unit fans 44 stop (S32). Next, the control device 60 outputs a fully closed signal to the all indoor side expansion valve 43. As a result, the entire indoor expansion valve 43 is fully closed (S33). When all the indoor side expansion valves 43 are fully closed, the flow of the refrigerant to the all indoor heat exchanger 41 is blocked. The process of S33 corresponds to the expansion valve fully closing process of the present invention.

  Next, the control device 60 outputs a closing operation signal to the hot gas bypass valve 21. As a result, the hot gas bypass valve 21 is closed (S34). In addition, when the hot gas bypass valve 21 is already closed at the time of performing the process of S34, the closed state of the hot gas bypass valve 21 is maintained. The process of S34 corresponds to the hot gas bypass valve closing process of the present invention.

  Then, the control apparatus 60 advances a process to S35, and performs a simultaneous defrost operation process. In this simultaneous defrosting operation process, the control device 60 determines the opening degree of the GHP first flow rate adjustment valve 20a, the opening degree of the GHP second flow rate adjustment valve 20b, and the opening degree of the EHP flow rate adjustment valve 39 of the outdoor heat exchanger. While controlling to the opening degree suitable for defrosting, the drive of the water pump provided in the cooling water piping through which the cooling water which cools the gas engine 11 distribute | circulates is controlled. In this simultaneous defrosting operation process, the control device 60 operates the GHP compressor 12 and the EHP compressor 32 so that the GHP outdoor heat exchanger 13 and the EHP outdoor heat exchanger 33 are simultaneously defrosted. Specifically, the rotational speed of the gas engine 11 is controlled so that the flow rate of the refrigerant discharged from the GHP compressor 12 becomes a flow rate suitable for defrosting of the GHP outdoor heat exchanger 13, and the refrigerant is discharged from the EHP compressor 32. The number of revolutions of the motor 31 is controlled so that the flow rate of the refrigerant becomes a flow rate suitable for defrosting of the EHP outdoor heat exchanger 33. In this specification, the operation operation in the GHP outdoor unit 10 and the EHP outdoor unit 30 by executing the simultaneous defrosting operation process is referred to as a simultaneous defrosting operation.

  When the simultaneous defrosting operation process is executed in S35, the high-temperature and high-pressure gas refrigerant discharged from the first discharge port 12b of the GHP compressor 12 enters the GHP four-way valve 16 via the GHP first pipe 15a. During the simultaneous defrosting operation, the switching state of the GHP four-way valve 16 is a cooling connection state, and the GHP first pipe 15a is connected to the GHP second pipe 15b in the GHP four-way valve 16, so that the GHP first pipe 15a The high-temperature and high-pressure gas refrigerant flowing into the GHP four-way valve 16 flows from the GHP four-way valve 16 to the GHP second pipe 15b. Then, the high-temperature and high-pressure gas refrigerant flows into the GHP outdoor heat exchanger 13 from the GHP second pipe 15b. The high-temperature and high-pressure gas refrigerant flows through the GHP outdoor heat exchanger 13, whereby the GHP outdoor heat exchanger 13 is heated. Thereby, the GHP outdoor heat exchanger 13 is defrosted.

  The refrigerant that has flowed through the GHP outdoor heat exchanger 13 flows into the GHP third pipe 15c (first connection pipe). Here, during the cooling operation, the refrigerant in the GHP third pipe 15c flows to the indoor heat exchanger 41 through the first liquid pipe 51, the indoor first pipe 42a, and the indoor expansion valve 43. During operation, the indoor expansion valve 43 is closed. Accordingly, during the simultaneous defrosting operation, the refrigerant in the GHP third pipe 15c (pipe L2) flows into the GHP seventh pipe 15g (sub pipe) connected to the GHP third pipe 15c. And it reaches the sub heat exchanger 19 via the GHP first flow rate adjusting valve 20a interposed in the GHP seventh pipe 15g. In the sub heat exchanger 19, the refrigerant exchanges heat with the cooling water. At this time, the refrigerant is heated by the heat of the cooling water (that is, the heat obtained by driving the gas engine 11).

  The refrigerant heated by the sub heat exchanger 19 flows into the GHP fourth pipe 15d (third connection pipe) from the GHP seventh pipe 15g, and is further supplied to the GHP accumulator 18 from the GHP fourth pipe 15d. In the GHP accumulator 18, the supplied refrigerant is gas-liquid separated. Only the low-temperature and low-pressure gas refrigerant flows out from the GHP accumulator 18 to the GHP fifth pipe 15e. The refrigerant that has flowed out of the GHP accumulator 18 to the GHP fifth pipe 15 e returns to the first suction port 12 a of the GHP compressor 12.

  Thus, the GHP outdoor heat exchanger 13 is defrosted by supplying the high-temperature and high-pressure gas refrigerant to the GHP outdoor heat exchanger 13 during the simultaneous defrosting operation. Further, the refrigerant is heated by the sub heat exchanger 19, so that a refrigerant having a higher temperature can be supplied to the GHP outdoor heat exchanger 13. Thereby, defrosting of the GHP outdoor heat exchanger 13 can be promoted.

  Further, when the simultaneous defrosting operation process is executed in S35, the high-temperature and high-pressure gas refrigerant discharged from the second discharge port 32b of the EHP compressor 32 passes through the EHP first pipe 35a to the EHP four-way valve 36. enter. At the time of the simultaneous defrosting operation, the switching state of the EHP four-way valve 36 is a connection state during cooling, and the EHP first pipe 35a is connected to the EHP second pipe 35b in the EHP four-way valve 36. The high-temperature and high-pressure gas refrigerant that has flowed into the EHP four-way valve 36 flows from the EHP four-way valve 36 to the EHP second pipe 35b. Then, the high-temperature and high-pressure gas refrigerant flows into the EHP outdoor heat exchanger 33 from the EHP second pipe 35b. When the high-temperature and high-pressure gas refrigerant flows through the EHP outdoor heat exchanger 33, the EHP outdoor heat exchanger 33 is heated. Thereby, the EHP outdoor heat exchanger 33 is defrosted.

  The refrigerant that has flowed through the EHP outdoor heat exchanger 33 flows into the EHP third pipe 35c (second connection pipe). The first liquid pipe 51 (the first liquid pipe 51 (the first liquid pipe 51) is then passed through the EHP flow rate adjusting valve 39 interposed in the middle of the EHP third pipe 35c, and further via the liquid pipe joint 30a and the second liquid pipe 53 of the EHP outdoor unit 30. 1 connection piping). Here, during the cooling operation, the refrigerant in the first liquid pipe 51 flows to the indoor heat exchanger 41 through the indoor first piping 42a and the indoor expansion valve 43, but during the simultaneous defrosting operation, the indoor expansion valve. 43 is closed. Therefore, during the simultaneous defrosting operation, the refrigerant in the first liquid pipe 51 flows through the GHP third pipe 15c in the GHP outdoor unit 10 via the liquid pipe joint 10a of the GHP outdoor unit 10, and further the GHP third pipe 15c. It flows from the (first connection pipe) to the GHP seventh pipe 15g (sub pipe) connected to the GHP third pipe 15c.

  Note that, as described above, the refrigerant discharged from the GHP compressor 12 during the simultaneous defrosting operation also flows into the GHP seventh pipe 15g via the GHP outdoor heat exchanger 13, so that the GHP seventh pipe 15g The refrigerant discharged from the GHP compressor 12 and the refrigerant discharged from the EHP compressor 32 merge. Thus, the refrigerant combined in the GHP seventh pipe 15g reaches the sub heat exchanger 19 via the GHP first flow rate adjustment valve 20a interposed in the GHP seventh pipe 15g. In the sub heat exchanger 19, the merged refrigerant exchanges heat with the cooling water. At this time, the refrigerant is heated by the heat of the cooling water (that is, the heat obtained by driving the gas engine 11).

  The refrigerant heated by the sub heat exchanger 19 flows from the GHP seventh pipe 15g into the GHP fourth pipe 15d (third connection pipe). In the GHP fourth pipe 15d, the refrigerant merged in the GHP seventh pipe 15g is branched. One of the divided refrigerant (refrigerant for the refrigerant discharged from the GHP compressor 12) is sucked into the GHP compressor 12 from the GHP fourth pipe 15d via the GHP accumulator 18 and the GHP fifth pipe as described above. The The other of the divided refrigerant (the refrigerant for the refrigerant discharged from the EHP compressor 32) flows into the GHP four-way valve 16 from the GHP fourth pipe 15d. At the time of the simultaneous defrosting operation, the switching state of the GHP four-way valve 16 is a cooling connection state, and the GHP fourth pipe 15d is connected to the GHP sixth pipe 15f at the GHP four-way valve 16, so that the GHP fourth pipe 15d The refrigerant that has flowed into the GHP four-way valve 16 flows from the GHP four-way valve 16 into the GHP sixth pipe 15f. The refrigerant that has flowed into the GHP sixth pipe 15f flows into the first gas pipe 52 via the gas pipe joint 10b of the GHP outdoor unit 10, and further from the first gas pipe 52 (third connection pipe) to the second gas pipe. 54 (fourth connection piping). The refrigerant in the second gas pipe 54 flows into the EHP sixth pipe 35f in the EHP outdoor unit 30 via the gas pipe joint 30b of the EHP outdoor unit 30, and further flows from the EHP sixth pipe 35f to the EHP four-way valve 36. enter. During the simultaneous defrosting operation, the switching state of the EHP four-way valve 36 is a cooling connection state, and the EHP sixth pipe 35f is connected to the EHP fourth pipe 35d at the EHP four-way valve 36. The refrigerant that has flowed into the EHP four-way valve 36 flows from the EHP four-way valve 36 to the EHP fourth pipe 35d. Then, the refrigerant is supplied to the EHP accumulator 38 from the EHP fourth pipe 35d.

  In the EHP accumulator 38, the supplied refrigerant is gas-liquid separated. Only the low-temperature and low-pressure gas refrigerant flows out from the EHP accumulator 38 to the EHP fifth pipe 35e. The refrigerant that has flowed out of the EHP accumulator 38 to the EHP fifth pipe 35 e returns to the second suction port 32 a of the EHP compressor 32.

  Thus, the high-temperature and high-pressure gas refrigerant is supplied to the EHP outdoor heat exchanger 33 during the simultaneous defrosting operation, whereby the EHP outdoor heat exchanger 13 is defrosted. The refrigerant that has flowed through the EHP outdoor heat exchanger 33 is also heated by the sub heat exchanger 19 together with the refrigerant that has flowed through the GHP outdoor heat exchanger 13. For this reason, a refrigerant having a higher temperature can be supplied to the EHP outdoor heat exchanger 33. Thereby, defrosting of the EHP outdoor heat exchanger 13 can be promoted. FIG. 5 is a schematic diagram of the air-conditioning apparatus 1 in which the refrigerant flow during the simultaneous defrosting operation is shown. In FIG. 5, the flow of the refrigerant discharged from the GHP compressor 12 is indicated by a solid line arrow, and the flow of the refrigerant discharged from the EHP compressor 32 is indicated by a broken line arrow.

  After executing the simultaneous defrosting operation process in S35, the control device 60 advances the process to S36 and determines whether or not the defrosting termination condition of the GHP outdoor unit 10 (GHP outdoor heat exchanger 13) is satisfied. to decide. As this defrosting termination condition, for example, the temperature of the refrigerant flowing into the GHP outdoor heat exchanger 13 during the simultaneous defrosting operation (that is, the temperature of the refrigerant flowing through the GHP second pipe 15b) is the temperature at which defrosting is considered to be completed. And the temperature of the refrigerant flowing out of the GHP outdoor heat exchanger 13 during the simultaneous defrosting operation (that is, the temperature of the refrigerant flowing through the GHP third pipe 15c) is considered to be complete. The temperature of the refrigerant flowing in the GHP outdoor heat exchanger 13 during the simultaneous defrosting operation is equal to or higher than the temperature that is determined as the temperature at which defrosting is considered to be completed. You can choose either.

  Since the GHP outdoor unit 10 includes the sub heat exchanger 19, the refrigerant flowing into the GHP outdoor heat exchanger 13 during the heating operation is appropriately heated by the sub heat exchanger 19. Therefore, the refrigerant flowing into the GHP outdoor heat exchanger 13 during the heating operation is warmer than the refrigerant flowing into the EHP outdoor heat exchanger 33 during the heating operation. Therefore, the GHP outdoor heat exchanger 13 is less likely to be frosted than the EHP outdoor heat exchanger 33, and even if it is frosted, it is easily defrosted. For this reason, when the simultaneous defrosting operation process is executed, the defrosting of the GHP outdoor heat exchanger 13 is normally completed prior to the defrosting of the EHP outdoor heat exchanger 33. That is, when the determination result in S36 is Yes, there is a high possibility that the defrosting of the EHP outdoor heat exchanger 33 has not been completed.

  When it is determined in S36 that the defrosting termination condition of the GHP outdoor unit 10 (GHP outdoor heat exchanger 13) is not satisfied (S36: No), the control device 60 continues the simultaneous defrosting operation process. While repeating (that is, continuing the simultaneous defrosting operation), the determination of S36 is repeated. On the other hand, if it is determined in S36 that the defrosting termination condition of the GHP outdoor unit 10 (GHP outdoor heat exchanger 13) is satisfied (S36: Yes), the control device 60 proceeds to S37 and performs hot gas bypass. An opening operation signal is output to the valve 21. Thereby, the hot gas bypass valve 21 is opened. By executing the process of S37, the simultaneous defrosting operation is performed with the hot gas bypass valve 21 opened. In addition, it is thought that the defrosting of the EHP outdoor heat exchanger 33 is not completed at the time of execution of the process of S37. That is, the process of S37 is a process of opening the hot gas bypass valve 21 when the defrosting of the EHP outdoor heat exchanger 33 is not completed. The process of S37 corresponds to the hot gas bypass valve opening process of the present invention.

  When the simultaneous defrosting operation is performed with the hot gas bypass valve 21 opened, a part of the high-temperature and high-pressure gas refrigerant discharged from the GHP compressor 12 passes through the hot gas bypass pipe 15h to the GHP fourth pipe 15d. Flowing. The refrigerant that has flowed through the hot gas bypass pipe 15h into the GHP fourth pipe 15d passes through the GHP accumulator 18 and the GHP fifth pipe 15e without passing through the GHP outdoor heat exchanger 13 and the sub heat exchanger 19. The air is sucked into the first suction port 12a of the compressor 12. For this reason, the flow rate of the refrigerant supplied from the GHP compressor 12 to the sub heat exchanger 19 decreases. When the flow rate of the refrigerant supplied from the GHP compressor 12 to the sub heat exchanger 19 decreases, the flow rate of the refrigerant supplied from the EHP compressor 32 to the sub heat exchanger 19 relatively increases. Thereby, the amount of heat given to the refrigerant discharged from the EHP compressor 32 in the sub heat exchanger 19 increases, and as a result, defrosting of the EHP outdoor heat exchanger 33 is further promoted.

  After opening the hot gas bypass valve in S37, the control device 60 proceeds to S38, and determines whether or not the defrosting termination condition of the EHP outdoor unit 30 (EHP outdoor heat exchanger 33) is satisfied. To do. As this defrosting termination condition, for example, the temperature of the refrigerant flowing into the EHP outdoor heat exchanger 33 during the simultaneous defrosting operation (that is, the temperature of the refrigerant flowing through the EHP second pipe 35b) is the temperature at which defrosting is considered to be completed. And the temperature of the refrigerant flowing out of the EHP outdoor heat exchanger 33 during the simultaneous defrosting operation (that is, the temperature of the refrigerant flowing through the EHP third pipe 35c) is considered to be complete. The temperature of the refrigerant flowing in the EHP outdoor heat exchanger 33 during the simultaneous defrosting operation is equal to or higher than the temperature that is predetermined as the temperature at which defrosting is considered to be completed. You can choose either.

  When it is determined in S38 that the defrosting termination condition of the EHP outdoor unit 30 (EHP outdoor heat exchanger 33) is not satisfied (S38: No), the control device 60 continues to execute the simultaneous defrosting operation process. However, the determination of S38 is repeated while continuing the simultaneous defrosting operation with the hot gas bypass valve 21 open. On the other hand, when it is determined in S39 that the defrosting termination condition of the EHP outdoor unit 30 (EHP outdoor heat exchanger 33) is satisfied (S38: Yes), the control device 60 proceeds to S39 and performs defrosting. Perform termination processing. By executing the defrosting termination process, the hot gas bypass valve 21 is closed and the switching state of the GHP four-way valve 16 and the EHP four-way valve 36 is returned from the cooling connection state to the heating connection state. Similarly to the normal heating operation, according to the air conditioning load, the rotation speed of the gas engine 11 and the motor 31, the rotation speed of the indoor unit fan 44, the opening degree of the indoor expansion valve 43, each flow control valve ( The opening degree of 20a, 20b, 39) is controlled. Thereafter, the control device 60 ends this routine.

  Moreover, the control apparatus 60 performs a single defrost process, when the single defrost flag is set to ON in S25 of the defrost preparation process of FIG. In this single defrosting process, the defrosting of an outdoor heat exchanger provided in an outdoor unit (hereinafter referred to as an “operating outdoor unit”) having an operating compressor is performed. First, a single defrosting process (EHP single defrosting process) when the cab outdoor unit is the EHP outdoor unit 30 will be described.

  FIG. 6 is a flowchart showing a flow of an EHP single defrost processing routine executed by the control device 60. When this routine is started, the control device 60 first changes the switching state of the EHP four-way valve 36 from the heating connection state to the cooling connection state in S41 of FIG. Next, a stop signal is output to the fan motor attached to all indoor unit fans 44 so that the rotation of all indoor unit fans 44 stops (S42). Thereby, the drive of all the indoor unit fans 44 stops. Next, the opening degree of the all-indoor expansion valve 43 is controlled so that the opening degree of the all-indoor expansion valve 43 becomes an opening degree suitable for heat exchange at the time of defrosting (an opening degree during EHP single defrosting). (S43).

  Thereafter, the control device 60 executes an EHP single defrosting operation process (S44). In this EHP single defrosting operation process, the control device 60 controls these valves so that the GHP first flow rate adjustment valve 20a and the GHP second flow rate adjustment valve 20b are closed, and is discharged from the EHP compressor 32. The motor 31 is controlled so that the flow rate of the refrigerant becomes a flow rate suitable for defrosting of the EHP outdoor heat exchanger 33. Thereby, EHP independent defrost operation is started.

  When the EHP single defrosting operation process is executed in S44, the refrigerant discharged from the second discharge port 32b of the EHP compressor 32 is the refrigerant discharged from the second discharge port 32b of the EHP compressor 32 during the cooling operation described above. Flows in the refrigerant circuit in the same way as For this reason, the high-temperature and high-pressure refrigerant gas discharged from the EHP compressor 32 is supplied to the EHP outdoor heat exchanger 33. Thereby, the EHP outdoor heat exchanger 33 is defrosted.

  After executing the EHP single defrosting operation process in S44, the control device determines whether or not the defrosting termination condition for the EHP outdoor unit 30 is satisfied (S45). When the termination condition is not satisfied (S45: No), the control device 60 repeats the determination of S45 while executing the EHP single defrosting operation process. On the other hand, when the termination condition is satisfied (S45: Yes), the control device 60 advances the process to S46 and executes the EHP single defrost termination process. Thereafter, the control device 60 ends this routine.

  Next, a single defrosting process (GHP single defrosting process) when the cab outdoor unit is the GHP outdoor unit 10 will be described. FIG. 7 is a flowchart showing the flow of the single defrosting process routine of the GHP outdoor unit 10 executed by the control device 60. When this routine is started, the control device 60 first changes the switching state of the GHP four-way valve 16 from the heating connection state to the cooling connection state in S51 of FIG. Next, a stop signal is output to the fan motor attached to all indoor unit fans 44 so that the rotation of all indoor unit fans 44 stops (S52). Thereby, the drive of all the indoor unit fans 44 stops. Next, the opening degree of the all-indoor expansion valve 43 is controlled so that the all-indoor expansion valve 43 is fully closed (S53).

  Thereafter, the control device 60 performs a GHP single defrosting operation process (S54). In this GHP single defrosting operation process, the control device 60 controls these valves so that the EHP flow rate adjustment valve 39 is closed, and the flow rate of the refrigerant discharged from the GHP compressor 12 is adjusted to the GHP outdoor heat exchanger 13. The gas engine 11 is controlled so that the flow rate is suitable for the defrosting. Thereby, GHP independent defrost operation is started.

  When the GHP single defrosting operation process is executed in S54, the refrigerant discharged from the first discharge port 12b of the GHP compressor 12 is discharged from the first discharge port 12b of the GHP compressor 12 during the above-described simultaneous defrosting operation. The refrigerant flows in the same manner as the refrigerant flow. For this reason, the high-temperature and high-pressure refrigerant gas discharged from the GHP compressor 12 is supplied to the GHP outdoor heat exchanger 13. Thereby, the GHP outdoor heat exchanger 13 is defrosted.

  After executing the GHP single defrosting operation process in S54, the control device determines whether or not a defrosting termination condition for the GHP outdoor unit 10 is satisfied (S55). When the termination condition is not satisfied (S55: No), the control device 60 repeats the determination of S55 while executing the GHP single defrosting operation process. On the other hand, when the end condition is satisfied (S55: Yes), the control device 60 advances the process to S56 and executes the GHP single defrosting end process. Thereafter, the control device 60 ends this routine.

  As described above, the air conditioner 1 according to the present embodiment is configured so that the GHP outdoor heat exchanger 13 and the EHP outdoor heat exchanger 33 can be defrosted simultaneously by the reverse cycle method. In the simultaneous defrosting process, not only the refrigerant discharged from the GHP compressor 12 but also the refrigerant discharged from the EHP compressor 32 is supplied to the sub heat exchanger 19 and heated by the sub heat exchanger 19. That is, according to this embodiment, the sub heat exchanger 19 can be used not only when the GHP outdoor heat exchanger 13 is defrosted but also when the EHP outdoor heat exchanger 33 is defrosted. For this reason, defrosting of the EHP outdoor heat exchanger 33 is promoted. Usually, the defrosting time of the EHP outdoor heat exchanger 33 is longer than the defrosting time of the GHP outdoor heat exchanger 13. Therefore, the defrosting time can be shortened by promoting the defrosting of the EHP outdoor heat exchanger 33 as shown in the present embodiment.

  Moreover, according to this embodiment, in the simultaneous defrosting process, when the defrosting of the GHP outdoor heat exchanger 13 is completed and the defrosting of the EHP outdoor heat exchanger 33 is not completed, the hot gas bypass valve 21 Opens. Thereby, a part of the refrigerant discharged from the GHP compressor 12 bypasses the sub heat exchanger 19. For this reason, the flow rate of the refrigerant supplied from the GHP compressor 12 to the sub heat exchanger 19 during the simultaneous defrosting operation decreases. Therefore, the flow rate of the refrigerant supplied from the EHP compressor to the sub heat exchanger can be relatively increased. As a result, the defrosting of the EHP outdoor heat exchanger 33 can be further promoted.

  The sub heat exchanger 19 is normally used for heating the refrigerant discharged from the GHP compressor 12 during the heating operation. Therefore, the sub heat exchanger 19 is designed based on the flow rate of the refrigerant discharged from the GHP compressor 12. However, during the simultaneous defrosting operation in the present embodiment, the refrigerant discharged from the GHP compressor 12 and the refrigerant discharged from the EHP compressor 32 merge in the GHP seventh pipe 15g, and the merged refrigerant enters the sub heat exchanger 19. It is sent. For this reason, the flow rate of the merged refrigerant may exceed the upper limit of the flow rate of the refrigerant that can flow to the sub heat exchanger 19. In this case, the refrigerant before flowing into the sub heat exchanger 19 may stay in the GHP seventh pipe 15g or the GHP outdoor heat exchanger 13. If the refrigerant stays in this way, the amount of refrigerant returning to the compressor (especially the GHP compressor 12) decreases, the pressure of the refrigerant sucked into the compressor (especially the GHP compressor 12) decreases, and the operation stops due to a low pressure abnormality. There is a risk of doing.

  In this regard, in the simultaneous defrosting process according to the present embodiment, the hot gas bypass valve 21 is set after the defrosting of the GHP outdoor heat exchanger 13 and before the defrosting of the EHP outdoor heat exchanger 33 is completed. Since the opening operation is performed, a part of the refrigerant discharged from the GHP compressor 12 bypasses the sub heat exchanger 19. For this reason, the flow rate of the refrigerant can be adjusted so that the flow rate of refrigerant flowing into the sub heat exchanger 19 during the simultaneous defrosting operation matches the flow rate of refrigerant flowing out of the sub heat exchanger 19. As a result, the low pressure abnormality as described above can be avoided.

  In the simultaneous defrosting process according to the present embodiment, the hot gas bypass valve 21 is closed before the simultaneous defrosting operation process (S35) is executed (S34). Therefore, the hot gas bypass valve 21 is closed at the start of the simultaneous defrosting operation. For this reason, the refrigerant discharged from the GHP compressor 12 is efficiently fed into the sub heat exchanger 19 without bypassing the sub heat exchanger 19. Thereby, defrosting of the GHP outdoor heat exchanger 13 can be promoted. Here, when the hot gas bypass valve 21 is closed, as described above, the flow rate balance between the flow rate of the refrigerant flowing into the sub heat exchanger 19 and the flow rate of the refrigerant flowing out of the sub heat exchanger 19 is lost. Although there is a possibility of causing a low pressure abnormality, the defrosting time of the GHP outdoor heat exchanger 13 is considerably shorter than the defrosting time of the EHP outdoor heat exchanger 33. Therefore, it is considered that the defrosting of the GHP outdoor heat exchanger 13 is completed before the low pressure abnormality occurs. After the defrosting of the GHP outdoor heat exchanger 13 is completed, the hot gas bypass valve 21 is opened to adjust the flow rate balance of the refrigerant flowing into and out of the sub heat exchanger 19. As a result, a low pressure abnormality can be avoided and the defrosting of the EHP outdoor heat exchanger 33 can be further promoted to shorten the defrosting time in the simultaneous defrosting process.

  As mentioned above, although embodiment of this invention was described, this invention should not be limited to the said embodiment. For example, in the above-described embodiment, the air conditioner 1 including one GHP outdoor unit 10 and one EHP outdoor unit 30 is illustrated. However, one or more GHP outdoor heat exchangers and one or more EHP outdoor heats are used. The present invention can be applied to an air conditioner including an exchanger. In the above embodiment, an example in which the GHP compressor 12 is operated by driving the gas engine 11 has been described. However, a gasoline engine or other internal combustion engine can be used instead of the gas engine 11. Moreover, although the said embodiment demonstrated the example in which the hot gas bypass valve 21 was closed at the time of the simultaneous defrost operation at the time of simultaneous defrost processing, the hot gas bypass valve 21 was always opened at the time of simultaneous defrost operation. May be. Thus, the present invention can be modified without departing from the gist thereof.

DESCRIPTION OF SYMBOLS 1 ... Air conditioning apparatus, 10 ... GHP outdoor unit, 10a ... Liquid pipe joint, 10b ... Gas pipe joint, 11 ... Gas engine (internal combustion engine), 11a ... Output shaft, 12 ... GHP compressor, 12a ... First inlet, 12b ... 1st discharge port, 13 ... GHP outdoor heat exchanger, 15a ... GHP 1st piping, 15b ... GHP 2nd piping, 15c ... GHP 3rd piping (1st connection piping), 15d ... GHP 4th piping (1st 3 connection piping), 15e ... GHP fifth piping (third connection piping), 15f ... GHP sixth piping (third connection piping), 15g ... GHP seventh piping (sub piping), 15h ... hot gas bypass piping, 16 ... GHP four-way valve (first switching valve), 161 ... first port, 162 ... second port, 163 ... third port, 164 ... fourth port, 17 ... GHP outdoor unit fan, 18 ... GHP accumulator 19 ... sub heat exchanger, 20 ... flow rate adjusting valve, 21 ... hot gas bypass valve, 30 ... EHP outdoor unit, 30a ... liquid pipe joint, 30b ... gas pipe joint, 31 ... motor (electric motor), 31a ... output Shaft, 32 ... EHP compressor, 32a ... second suction port, 32b ... second discharge port, 33 ... EHP outdoor heat exchanger, 35a ... EHP first piping, 35b ... EHP second piping, 35c ... EHP third piping ( Second connection piping), 35d ... EHP fourth piping (fourth connection piping), 35e ... EHP fifth piping (fourth connection piping), 35f ... EHP sixth piping (fourth connection piping), 36 ... EHP four-way valve (Second switching valve), 361 ... first port, 362 ... second port, 363 ... third port, 364 ... fourth port, 37 ... EHP outdoor unit fan, 38 ... EHP accumulator, 40 ... indoor unit, 4 a ... liquid pipe joint, 40b ... gas pipe joint, 41, 41A, 41B, 41C ... indoor heat exchanger, 42a ... indoor side first pipe (first connection pipe), 42b ... indoor side second pipe (third connection) Piping), 43 ... indoor side expansion valve, 44 ... indoor unit fan, 51 ... first liquid pipe (first connecting pipe), 52 ... first gas pipe (third connecting pipe), 53 ... second liquid pipe (first) (Two connection piping), 54 ... second gas pipe (fourth connection piping), 60 ... control device, S31 ... connection state switching processing, S33 ... expansion valve full closing processing, S34 ... hot gas bypass valve closing processing, S35 ... Simultaneous defrosting operation processing, S37 ... Hot gas bypass valve opening processing

Claims (3)

An internal combustion engine, having a first suction port and a first discharge port, is operated by driving the internal combustion engine, sucks refrigerant from the first suction port, and compresses and compresses the sucked refrigerant. A GHP compressor that discharges from a discharge port; and a refrigerant that is connected to the first suction port of the GHP compressor during cooling operation and connected to the first discharge port of the GHP compressor during cooling operation, The GHP outdoor heat exchanger for heat exchange, the connection state between the GHP outdoor heat exchanger and the GHP compressor, the heating connection state where the GHP outdoor heat exchanger is connected to the first inlet, and the first A GHP outdoor unit having a first switching valve that can be switched to a cooling connection state connected to the discharge port;
An electric motor and a second suction port and a second discharge port, which are operated by driving the motor to suck in the refrigerant from the second suction port and compress the compressed refrigerant and compress the compressed refrigerant into the second discharge port The EHP compressor that discharges from the air, and is connected to the second suction port of the EHP compressor during heating operation and connected to the second discharge port of the EHP compressor during cooling operation, and exchanges heat between the refrigerant flowing through the interior and the outside air An EHP outdoor heat exchanger, a connection state between the EHP outdoor heat exchanger and the EHP compressor, a heating connection state where the EHP outdoor heat exchanger is connected to the second suction port, and the second discharge port. An EHP outdoor unit having a second switching valve that can be switched to a connected state during cooling that is connected to
When the switching state of both the first switching valve and the second switching valve is the heating state connection state, the first switching valve and the second discharge port of the EHP compressor are connected to the first discharge port of the GHP compressor and The first switching valve and the second switching valve are both connected to the first suction port of the GHP compressor and the second suction port of the EHP compressor when the switching state of the first switching valve and the second switching valve are both in the cooling state. An indoor heat exchanger for exchanging heat between the refrigerant circulating in the interior and the indoor air, and adjusting the flow rate of the refrigerant flowing through the indoor heat exchanger and the refrigerant flowing out of the indoor heat exchanger or the indoor heat exchanger An indoor unit having an expansion valve for expanding the inflowing refrigerant;
A first connection pipe connecting the indoor heat exchanger and the GHP outdoor heat exchanger;
A second connection pipe for connecting the first connection pipe and the EHP outdoor heat exchanger;
A third connection pipe for connecting the indoor heat exchanger to the first suction port of the GHP compressor when the switching state of the first switching valve is the connection state during cooling;
A fourth connection pipe that connects the third connection pipe and the second suction port of the EHP compressor when the switching state of the second switching valve is the cooling-time connection state;
A sub-pipe that is provided in the GHP outdoor unit and connects the first connection pipe and the third connection pipe;
A sub heat exchanger that is provided in the GHP outdoor unit, is interposed in the sub pipe, and heats the refrigerant flowing in the sub pipe by heat obtained by driving the internal combustion engine;
A control device for controlling the first switching valve, the second switching valve, and the expansion valve;
With
The control device is configured to perform a simultaneous defrosting process for simultaneously defrosting the GHP outdoor heat exchanger and the EHP outdoor heat exchanger,
In the simultaneous defrosting process, the control device performs a connection state switching process for switching the connection state of the first switching valve and the second switching valve to the connection state during cooling, and an expansion for fully closing the expansion valve. Performing a valve fully closing process and a simultaneous defrosting operation process for operating the GHP compressor and the EHP compressor so that the GHP outdoor heat exchanger and the EHP outdoor heat exchanger are defrosted simultaneously;
Air conditioner. In the air conditioning apparatus according to claim 1,
Provided in the GHP outdoor unit, a hot gas bypass pipe connecting the first discharge port and the first suction port;
A hot gas bypass valve interposed in the hot gas bypass pipe and permitting or blocking the flow of the refrigerant in the hot gas bypass pipe,
The control device executes a hot gas bypass valve opening process for opening the hot gas bypass valve when at least the defrosting of the EHP outdoor heat exchanger is not completed in the simultaneous defrosting process. , Air conditioner. In the air conditioning apparatus according to claim 1 or 2,
The said control apparatus is an air conditioning apparatus which performs the hot gas bypass valve closing process which closes the said hot gas bypass valve before execution of the said simultaneous defrost operation process by the said simultaneous defrost process.

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