JP2015152246A - air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve a problem that frost formation is found only on an air heat exchanger of a power supply driven outdoor unit, in a case when the electric power supply driven outdoor unit incorporating an electric power supply driven compressor and a non-electric power supply driven outdoor unit incorporating a non-electric power supply driven compressor are installed together with each other.SOLUTION: An electric power supply driven outdoor unit decompression device 115 of an electric power supply driven outdoor unit 100 is closed, so that a refrigerant to be evaporated in an outdoor heat exchanger 130 is evaporated by an outdoor heat exchanger 230 of a non-electric power supply driven outdoor unit 200 and an engine exhaust-heat heat exchanger 217. The refrigerant evaporated by the outdoor heat exchanger 230 and the engine exhaust-heat heat exchanger 217 is returned to a non-electric power supply driven compressor 211, and is also returned to the electric power supply driven compressor 111 through an inter-outdoor unit suction communication pipe 240 by opening a suction communication pipe opening/closing valve 245.

Description

The present invention relates to an air conditioner provided with an outdoor unit incorporating a non-power source driven compressor driven by an engine and an outdoor unit incorporating a power source driven compressor driven by electric power.

Generally, a multi-type air conditioner is known in which a plurality of outdoor unit groups and a plurality of indoor unit groups are connected by piping, and the number of outdoor units operated is controlled according to the air conditioning load. As an electric drive outdoor unit with a built-in power-driven compressor and a non-power-drive outdoor unit with a built-in non-power-driven compressor, it can be expanded even when there is not enough power capacity. A so-called hybrid air conditioner that can achieve leveling has been proposed. (For example, refer patent document 1, FIG. 3).

  When the gas heat pump is partially loaded, the thermal efficiency of the gas engine is reduced, and the operating efficiency of the air conditioner is reduced. In order to avoid this, the displacement volume of the non-power source driven compressor driven by the gas engine is made larger than that of the power source driven compressor, the power source driven compressor is mainly operated during partial load, and the gas engine is operated at high load. A control method for driving the main body has also been proposed (see, for example, Patent Document 2).

JP-A-5-340624 JP 2003-56931 A

  However, when using a combination of a non-electrically driven outdoor unit that incorporates a non-powered compressor having a larger displacement volume than a power-driven compressor and an electrically driven outdoor unit, for example, the rated capacity of the non-powered compressor 20HP and the rated capacity of the power-driven compressor is 10HP, which is 30HP in total. When heating operation is performed at about 30HP at low outside air temperature (for example, outside air temperature 2 ° C), only the air heat exchanger of the power-powered outdoor unit Risk of frost formation.

  During the heating operation, both the electrically driven outdoor unit and the non-electrically driven outdoor unit exchange heat with the outside air to evaporate the refrigerant. However, the non-power source driven outdoor unit has a configuration for evaporating the refrigerant by effectively using the exhaust heat of the compressor drive source (gas engine, etc.), and the non-power source driven compressor is located near the maximum capacity. The air heat exchanger does not frost even when it is in operation. On the other hand, there is no exhaust heat that can be effectively utilized in the power supply outdoor unit, and it is necessary to evaporate all the refrigerant with an air heat exchanger. When operating a power supply outdoor unit near the maximum capacity, the temperature of the refrigerant flowing through the air heat exchanger is lowered to 0 ° C. or lower in order to increase the heat exchange capacity (evaporation capacity) in the air heat exchanger of the outdoor unit. The necessity arises, the moisture in the outside air freezes on the fin surface of the air heat exchanger, and frosting occurs.

  Therefore, when heating operation is performed in the vicinity of the maximum capacity (30 HP), only the outdoor heat exchanger of the power supply outdoor unit has to be frosted and defrosted. During the defrosting, there is a problem that the heating capacity of the entire air conditioner decreases and the comfort of the user is impaired.

The present invention solves the above-mentioned problem, and in an air conditioner that combines an outdoor unit incorporating a non-power-driven compressor and an outdoor unit incorporating a power-driven compressor, the power-driven compressor is used during heating. Provided is an air conditioner that prevents continuous refrigeration in the air heat exchanger of the outdoor unit with built-in, prevents frost formation in the air heat exchanger, and enables continuous operation while maintaining heating capacity For the purpose.

  It is another object of the present invention to provide an air conditioner that can quickly defrost and quickly recover heating capacity even if the outdoor heat exchanger of the power supply outdoor unit is frosted.

  In order to solve the above problems, the first and second aspects of the present invention provide a power-driven outdoor unit suction pipe through which a refrigerant sucked by the power-driven compressor flows in the power-driven outdoor unit, and a non-power-driven compression in the non-power-driven outdoor unit. An outdoor unit suction connection pipe connecting the non-power supply outdoor unit suction pipe through which the refrigerant sucked by the machine flows, and a power drive outdoor unit suction pipe and a non-power supply outdoor unit suction pipe in the middle of the outdoor unit suction communication pipe A first on-off valve for controlling the communication between the two, and the first on-off valve is opened during heating operation, and a part of the refrigerant discharged from the outdoor heat exchanger of the non-power-driven outdoor unit is supplied to the power source of the power-driven outdoor unit It is made to flow through the drive compressor.

The third and fourth inventions include a power source driving outdoor unit equipped with a power source driven compressor driven by electric power, and a non power source driving outdoor unit equipped with a non power source driving compressor driven by a driving source other than electric power. In an air conditioner connected in parallel to an inter-unit pipe extending from at least one indoor unit, the power-driven outdoor unit discharge pipe through which the refrigerant discharged from the power-driven compressor flows in the power-driven outdoor unit, In the power supply outdoor unit, an outdoor unit discharge communication pipe connecting the non-power supply outdoor unit discharge pipe through which the refrigerant discharged from the non-power supply compressor flows is provided, and the power supply drive outdoor unit is provided in the middle of the outdoor unit discharge communication pipe. A second on-off valve that controls communication between the unit discharge pipe and the non-power-driven outdoor unit discharge pipe; When defrosting the outdoor heat exchanger, this second on-off valve is opened so that a part of the refrigerant discharged from the compressor of the non-power-driven outdoor unit flows into the outdoor heat exchanger of the power-driven outdoor unit. is there.

  In a fifth aspect of the present invention, the excluded volume of the non-power source driven compressor is larger than the excluded volume of the power source driven compressor.

  According to the first and second inventions, at the time of heating, a part of the refrigerant to be evaporated in the outdoor heat exchanger of the power supply driven outdoor unit is caused to flow to the non-power supply driven outdoor unit, and the outdoor heat exchanger of the non-power supply driven outdoor unit; And it evaporates with the waste heat which generate | occur | produces from the drive source of a non-power source drive compressor. The refrigerant evaporated in the non-power-driven outdoor unit is returned to the non-power-driven compressor, and the first on-off valve is opened and returned to the power-driven compressor through the outdoor unit intake communication pipe. Therefore, the amount of refrigerant flowing in the outdoor heat exchanger of the power supply outdoor unit is reduced, and the amount of heat exchange for evaporating the refrigerant is reduced, so that frost formation in the outdoor heat exchanger of the power supply outdoor unit can be prevented. And heating capacity can be maintained.

  According to the third and fourth inventions, when the outdoor heat exchanger of the power supply outdoor unit is frosted during the heating operation, the power supply outdoor unit and the non-power supply outdoor unit are switched to the cooling operation, and the discharge connection pipe between the outdoor units Since the refrigerant discharged from the non-power source driven compressor flows through the outdoor heat exchanger of the power source driven outdoor unit, the power source driven compressor is included in the outdoor heat exchanger of the power source driven outdoor unit. Since the defrosting is carried out by flowing more high-temperature and high-pressure refrigerant than when only the refrigerant discharged by is discharged, the defrosting can be completed quickly and the heating capacity of the air conditioner can be quickly restored. Can do.

It is a refrigerating cycle figure of the air conditioner in Embodiment 1 of this invention. It is a refrigerating cycle figure of the air conditioner in Embodiment 2 of this invention. It is a refrigerating cycle figure of the air conditioner in a prior art.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, this invention is not limited by this embodiment.
(Embodiment 1)
A refrigeration cycle configuration of the air conditioner of the present embodiment is shown in FIG. The air conditioner of FIG. 1 has two indoor units for a total of two units: a power source driven outdoor unit 100 equipped with a power source driven compressor as an outdoor unit and a non power source driven outdoor unit 200 equipped with a non power source driven compressor. It is a connected so-called multi-type air conditioner. The refrigeration cycle configuration is not limited to that shown in FIG. For example, three or more outdoor units and three or more indoor units can be connected in parallel.

  The power source driving outdoor unit 100 and the non-power source driving outdoor unit 200 are connected to the indoor units 300 and 310 by piping through which the refrigerant flows.

  In the power-driven outdoor unit 100, 111 is a power-driven compressor that is driven by electric power such as commercial power, and 112 is an accumulator that supplies a gas refrigerant to the power-driven compressor 111. A power drive outdoor unit oil separator 113 separates refrigeration oil contained in the discharge gas of the power drive compressor 111. The refrigerating machine oil separated by the power supply driven outdoor unit oil separator 113 is returned to the suction pipe of the power supply driven compressor 111 by the oil return pipe 113a. The communication of the oil return pipe 113a is controlled by opening and closing the oil return pipe opening / closing valve 113b.

  114 is a power-driven outdoor unit four-way valve that switches between refrigeration cycles by cooling and heating, and 115 is a power-driven outdoor unit decompression device that expands the refrigerant. Reference numeral 120 denotes an outdoor fan that supplies air around the power supply outdoor unit 100 to the outdoor heat exchanger 130. As the outdoor heat exchanger 130, a so-called fin-and-tube heat exchanger is used in which a copper inner grooved tube is passed through an aluminum fin.

  In the non-power source drive outdoor unit 200, 210 is an engine using, for example, gas as a drive source, and 211 is an engine drive compressor that compresses refrigerant by obtaining driving force from the engine 210. The displacement volume of the engine driven compressor 211 is larger than the displacement volume of the power supply driven compressor 111. The lubricating oil for the engine driven compressor 211 and the power source driven compressor 111 is the same refrigerating machine oil.

  An accumulator 212 supplies a gas refrigerant to the engine driven compressor 211. Reference numeral 213 denotes a non-power source driven outdoor unit oil separator that separates refrigeration oil contained in the discharge gas of the engine driven compressor 211. The refrigerating machine oil separated by the non-power source drive outdoor unit oil separator 213 is returned to the suction pipe of the engine drive compressor 211 by the oil return pipe 213a. The communication of the oil return pipe 213a is controlled by opening and closing the oil return pipe on-off valve 213b.

Reference numeral 214 denotes a non-power source driven outdoor unit four-way valve that switches the refrigeration cycle between cooling and heating, and reference numeral 215 denotes a non-power source driven outdoor unit decompression device that expands the refrigerant. Reference numeral 217 denotes an engine exhaust heat exchanger that performs heat exchange between the high-temperature coolant used for cooling the engine 211 and the refrigerant, and is used during heating. A plate heat exchanger or the like is used as the engine exhaust heat exchanger 217. Reference numeral 216 denotes a refrigerant flow rate adjusting valve for the engine exhaust heat exchanger that adjusts the flow rate of the refrigerant flowing into the engine exhaust heat exchanger 217.

  Reference numeral 220 denotes an outdoor fan that supplies air around the non-power-driven outdoor unit 200 to the outdoor heat exchanger 230. As the outdoor heat exchanger 230, a so-called fin-and-tube heat exchanger is used in which a copper inner grooved tube is passed through an aluminum fin.

  In the indoor unit 300, 301 is an indoor air heat exchanger, 302 is an indoor fan that supplies air around the indoor unit 300 to the indoor air heat exchanger 301, and 303 is an indoor unit decompression device that expands the refrigerant. Similarly, in the indoor unit 310, 311 is an indoor air heat exchanger, 312 is an indoor fan that supplies the air around the indoor unit 310 to the indoor air heat exchanger 311, and 313 is an indoor unit decompression device that expands the refrigerant. .

  In the present embodiment, among the pipes connected to the accumulator 112 of the power source driven outdoor unit 100, the pipes on the opposite side to the power source driven compressor 111 and the pipes connected to the accumulator 212 of the non-power source driven outdoor unit 200 Among these, the pipe on the opposite side to the engine-driven compressor 211 is connected by an outdoor unit inter-unit suction communication pipe 240. The outdoor unit suction communication pipe 240 is provided with a suction communication pipe opening / closing valve 245 for controlling the communication.

  Next, operations of the power supply driving outdoor unit 100, the non-power supply driving outdoor unit 200, and the indoor units 300 and 310 will be described.

  During the cooling operation, the power-driven outdoor unit four-way valve 114 and the non-power-driven outdoor unit four-way valve 214 are set so that the refrigerant flows through a solid line (see FIG. 1). The engine exhaust heat exchanger refrigerant flow rate adjustment valve 216 is closed, and no refrigerant flows into the engine exhaust heat exchanger 217. Further, the suction communication pipe opening / closing valve 245 is closed, and the refrigerant does not flow through the outdoor unit suction communication pipe 240.

  In the power drive outdoor unit 100, the high-temperature and high-pressure refrigerant compressed by the power drive compressor 111 first flows into the power drive outdoor unit oil separator 113. The high-purity gas refrigerant from which the refrigeration oil is separated in the power supply outdoor unit oil separator 113 passes through the power supply outdoor unit four-way valve 114 and enters the outdoor heat exchanger 130. In the outdoor heat exchanger 130, the gas refrigerant exchanges heat with the outside air to dissipate heat, condenses, becomes high-pressure liquid refrigerant, passes through the power-driven outdoor unit decompression device 115, and is supplied to the indoor units 300 and 310. .

  The refrigerating machine oil separated by the power drive outdoor unit oil separator 113 is returned to the suction pipe of the power drive compressor 111 by opening the oil return pipe on / off valve 113b.

  In the non-power-driven outdoor unit 200, the high-temperature and high-pressure refrigerant compressed by the engine-driven compressor 211 first flows into the non-power-driven outdoor unit oil separator 213. The high-purity gas refrigerant from which the refrigerating machine oil has been separated in the non-power source driven outdoor unit oil separator 213 passes through the non-power source driven outdoor unit four-way valve 214 and enters the outdoor heat exchanger 230. In the outdoor heat exchanger 230, the gas refrigerant exchanges heat with the outside air to dissipate heat, condenses, becomes high-pressure liquid refrigerant, passes through the non-power-driven outdoor unit decompression device 215, and is supplied to the indoor units 300 and 310. The

  The refrigerating machine oil separated by the power drive outdoor unit oil separator 113 is returned to the suction pipe of the power drive compressor 111 by opening the oil return pipe on / off valve 113b.

The high-pressure liquid refrigerant that has entered the indoor unit 300 is depressurized by the indoor unit decompression device 303, enters a gas-liquid two-phase state, and flows into the indoor heat exchanger 301. The refrigerant in the gas-liquid two-phase state is the indoor heat exchanger 3
At 01, heat is exchanged with the air in the air-conditioning target, absorbs heat, evaporates, and flows out from the indoor unit 300 as a gas refrigerant.

  Also in the indoor unit 310, as in the indoor unit 300, first, the high-pressure liquid refrigerant is decompressed by the indoor unit decompression device 213, enters a gas-liquid two-phase state, and flows into the indoor heat exchanger 311. In the indoor heat exchanger 311, the refrigerant in the gas-liquid two-phase state evaporates after exchanging heat with the air in the space to be air-conditioned and then flows out from the indoor unit 310 as a gas refrigerant.

  When only the indoor unit 300 performs the cooling operation, the indoor unit decompression device 313 is closed and the refrigerant is not supplied to the indoor heat exchanger 311 of the indoor unit 310. On the other hand, when only the indoor unit 310 performs the cooling operation, the indoor unit decompression device 303 is closed and the refrigerant is not supplied to the indoor heat exchanger 301 of the indoor unit 300.

  The gas refrigerant flowing out from the indoor units 300 and 310 returns to the power supply outdoor unit 100 and the non-power supply outdoor unit 200 again. The gas refrigerant flowing into the power supply driven outdoor unit 100 returns to the power supply driven compressor 111 through the four-way valve 114 and the accumulator 112. Further, the gas refrigerant flowing into the non-power source drive outdoor unit 200 passes through the four-way valve 214 and the accumulator 212 and returns to the engine drive compressor 211.

  The operation method of the power supply driven compressor 111 and the engine driven compressor 211 during the cooling operation is, for example, as follows.

  If the cooling load is smaller than the cooling capacity when the engine-driven compressor 211 is operated at the minimum operating frequency (the minimum cooling capacity of the engine-driven compressor 211), the engine-driven compressor 211 alone will cause intermittent operation. Only the power supply driven compressor 111 is operated.

  The cooling capacity when the cooling load is larger than the minimum cooling load of the engine-driven compressor 211 and both the power-driven compressor 111 and the engine-driven compressor 211 are operated at the minimum operating frequency (when both compressors are operated). If it is smaller than the minimum cooling capacity), one of the power source driven compressor 111 and the engine driven compressor 211, for example, the one with the lower operating cost or the lower energy consumption is selected for operation.

  When the cooling load is larger than the minimum cooling capacity during operation of both compressors, both the power-driven compressor 111 and the engine-driven compressor 211 are operated so that, for example, the operating cost or energy consumption is minimized. To do. In this case, in order to determine the operating frequency of the power supply driven compressor 111 and the engine driven compressor 211 for minimizing the operating cost or the energy consumption, the operating frequency and operating cost of each compressor or the energy consumption Use the relationship.

  Actually, the ratio of the cooling load that the engine-driven compressor 211 has to the overall cooling load is the maximum cooling capacity when both compressors are operated at the maximum operating frequency (maximum cooling capacity when both compressors are operating). On the other hand, the ratio of the cooling capacity when only the engine driven compressor 211 is operated at the maximum operating frequency is about ± 15%.

  Next, during the heating operation, the power-driven outdoor unit four-way valve 114 and the non-power-driven outdoor unit four-way valve 214 are set so that the refrigerant flows along the dotted line (see FIG. 1). Further, the suction communication pipe opening / closing valve 245 is in an open state, and a refrigerant flows through the outdoor unit suction communication pipe 240.

In the power drive outdoor unit 100, the high-temperature and high-pressure refrigerant compressed by the power drive compressor 111 first flows into the power drive outdoor unit oil separator 113. The high-purity gas refrigerant from which the refrigeration oil is separated in the power drive outdoor unit oil separator 113 passes through the power drive outdoor unit four-way valve 114, exits the power drive outdoor unit 100, and is supplied to the indoor units 300 and 310. The

  The refrigerating machine oil separated by the power drive outdoor unit oil separator 113 is returned to the suction pipe of the power drive compressor 111 by opening the oil return pipe on / off valve 113b.

  In the non-power-driven outdoor unit 200, the high-temperature and high-pressure refrigerant compressed by the engine-driven compressor 211 first flows into the non-power-driven outdoor unit oil separator 213. In the non-power-driven outdoor unit oil separator 213, the high-purity gas refrigerant from which the refrigeration oil has been separated passes through the non-power-driven outdoor unit four-way valve 214, exits the power-driven outdoor unit 200, and enters the indoor units 300 and 310. Supplied.

  The high-temperature and high-pressure gas refrigerants sent from the power source driving outdoor unit 100 and the non-power source driving outdoor unit 200 are combined and then supplied to the indoor units 300 and 310. The high-temperature and high-pressure gas refrigerant that has entered the indoor unit 300 flows into the indoor heat exchanger 301. The high-temperature and high-pressure gas refrigerant exchanges heat with the air in the space to be air-conditioned in the indoor heat exchanger 301, dissipates the heat, and then condenses into a high-pressure liquid refrigerant that passes through the indoor unit decompression device 303. , Out of the indoor unit 300.

  Also in the indoor unit 310, as in the indoor unit 300, first, the high-temperature and high-pressure gas refrigerant flows into the indoor heat exchanger 311. In the indoor heat exchanger 311, the high-temperature and high-pressure gas refrigerant exchanges heat with the air in the air-conditioned space, dissipates heat, condenses, becomes high-pressure liquid refrigerant, and passes through the indoor unit decompression device 313. , Out of the indoor unit 310.

  As in the case of cooling, when only the indoor unit 300 performs the heating operation, the indoor unit decompression device 313 is closed and the refrigerant is not supplied to the indoor heat exchanger 311 of the indoor unit 310. On the other hand, when only the indoor unit 310 performs the heating operation, the indoor unit decompression device 303 is closed and the refrigerant is not supplied to the indoor heat exchanger 301 of the indoor unit 300.

  After the high-pressure liquid refrigerant that has flowed out of the indoor units 300 and 310 merges, the high-pressure liquid refrigerant returns to the power supply outdoor unit 100 and the non-power supply outdoor unit 200 again. At this time, the power drive outdoor unit decompression device 115 of the power drive outdoor unit 100 is fully closed or substantially closed, and the amount of refrigerant flowing in the outdoor heat exchanger 130 of the power drive outdoor unit 100 is determined by the non-power supply. This is considerably smaller than the sum of the refrigerant amount flowing in the outdoor heat exchanger 230 of the drive outdoor unit 200 and the refrigerant amount flowing in the engine exhaust heat exchanger 217.

  For example, when the maximum heating capacity when the engine-driven compressor 211 is operated at the maximum operating frequency is set to twice the maximum heating capacity when the power-driven compressor 111 is operated at the maximum operating frequency, the heating load As will be described later, the ratio of the heating load that the power supply driven compressor 111 is responsible for to the whole is approximately proportional to the maximum heating capacity of each compressor, and is approximately ½ of the heating load that the non-power supply driven compressor 211 is responsible for. Become. That is, the amount of refrigerant originally flowing in the outdoor heat exchanger 130 of the power source driven outdoor unit 100 is approximately ½ of the amount of refrigerant flowing in the outdoor heat exchanger 230 and the engine exhaust heat heat exchanger 217 of the non-power source driven outdoor unit 200. It becomes.

However, in the present embodiment, the amount of refrigerant flowing in the outdoor heat exchanger 130 of the power source driven outdoor unit 100 is 1 of the amount of refrigerant flowing in the outdoor heat exchanger 230 and the engine exhaust heat exchanger of the non-power source driven outdoor unit 200. It is set to an amount considerably smaller than / 2, for example, 1/4 or less. In order to evaporate all the refrigerant flowing through the outdoor heat exchanger 130 by reducing the amount of refrigerant flowing through the outdoor heat exchanger 130 of the power supply outdoor unit 100, the temperature of the refrigerant does not have to be lowered.
That is, moisture in the outside air hardly freezes on the fin surface of the outdoor heat exchanger 130, and frost formation hardly occurs.

  During the heating operation, the suction communication pipe opening / closing valve 245 of the non-power-driven outdoor unit 200 is in an open state, and a part of the refrigerant evaporated in the outdoor heat exchanger 230 passes through the four-way valve 214. Then, it flows into the outdoor unit suction communication pipe 240, passes through the accumulator 112, and returns to the power supply driven compressor 111.

  The operation method of the power supply driven compressor 111 and the engine driven compressor 211 during the heating operation is, for example, as follows.

  If the heating load is smaller than the heating capacity when the engine-driven compressor 211 is operated at the minimum operating frequency (the minimum heating capacity of the engine-driven compressor 211), the engine-driven compressor 211 alone will cause intermittent operation. Only the power supply driven compressor 111 is operated.

  Heating capacity when the heating load is larger than the minimum heating load of the engine-driven compressor 211 and both the power-driven compressor 111 and the engine-driven compressor 211 are operated at the minimum operating frequency (during both compressor operations) If it is smaller than (minimum heating capacity), one of the power source driven compressor 111 and the engine driven compressor 211, for example, the one with the lower operating cost or the lower energy consumption is selected for operation.

  When the heating load is larger than the minimum heating capacity during operation of both compressors, both the power-driven compressor 111 and the engine-driven compressor 211 are operated so that, for example, the operating cost or energy consumption is minimized. To do. In this case, in order to determine the operating frequency of the power source driven compressor 111 and the engine driven compressor 211 for minimizing the operating cost or energy consumption, the operating frequency and operating cost of each compressor or the energy consumption Use the relationship. Actually, the ratio of the heating load that the engine-driven compressor 211 has to the overall heating load is the maximum heating capacity when both compressors are operated at the maximum operating frequency (maximum heating capacity when operating both compressors). On the other hand, the ratio of the heating capacity when only the engine-driven compressor 211 is operated at the maximum operating frequency is about ± 15%.

  However, during the heating operation, the frost formation state of the outdoor heat exchanger 230 of the non-power-driven outdoor unit 200 is constantly monitored, and if there is a risk of frost formation, the operation cost or energy consumption is minimized. Even if the operating frequency of each compressor is set so as to be, control is performed to increase the operating frequency of the engine-driven compressor 211 and lower the operating frequency of the power-driven compressor 111. When the operating frequency of the engine-driven compressor 211 is increased, the amount of exhaust heat of the engine 210 increases, and the amount of heat of cooling water supplied to the engine exhaust heat heat exchanger 217 also increases. That is, the engine exhaust heat exchanger 217 can evaporate more refrigerant, reducing the amount of refrigerant flowing to the outdoor heat exchanger 230 and reducing the risk of frost formation.

  As apparent from the above description, in the present embodiment, during heating, a part of the refrigerant to be evaporated in the outdoor heat exchanger 130 of the power supply outdoor unit 100 is exchanged with the outdoor heat of the non-power supply outdoor unit 200. The evaporator 230 and the engine exhaust heat exchanger 217 evaporate. The refrigerant evaporated in the outdoor heat exchanger 230 and the engine exhaust heat exchanger 217 is returned to the non-power source driven compressor 211 and the suction communication pipe opening / closing valve 245 is opened to supply power through the outdoor unit suction communication pipe 240. The drive compressor 111 is also returned.

  Therefore, during heating operation, the amount of refrigerant flowing in the outdoor heat exchanger 130 of the power supply outdoor unit 110 is reduced, and the amount of heat exchange for evaporating the refrigerant is reduced, so that frost formation in the outdoor heat exchanger 130 is prevented. And heating capacity can be maintained.

Further, by reducing or eliminating the heat exchange amount in the outdoor heat exchanger 130 of the power supply outdoor unit 110, the rotational speed of the outdoor fan 120 can be reduced or made zero. Therefore, it is possible to suppress the power consumption of the outdoor blower fan 120 and improve the efficiency of the entire air conditioner.
(Embodiment 2)
A refrigeration cycle diagram of the air conditioner in the present embodiment is shown in FIG. Compared with FIG. 1, FIG. 2 does not have the outdoor unit suction communication pipe 240 and the suction communication pipe on / off valve 245, and instead has the outdoor unit heating suction communication pipe 241 and the heating suction communication pipe on / off valve 246. To do. Since other configurations are the same as those in FIG. 1, description of the components is omitted.

  As shown in FIG. 1, the intake communication pipe 241 during heating between the outdoor units is connected to a pipe between the outdoor heat exchanger 130 and the four-way valve 114 in the power-driven outdoor unit 100 and outdoor heat exchange in the non-power-driven outdoor unit 200. 230, and a pipe connecting the pipe between the engine exhaust heat exchanger 217 and the four-way valve 214. The outdoor unit suction communication pipe 240 is provided with a heating suction communication pipe opening / closing valve 246 for controlling the communication.

  Next, operations of the power supply driving outdoor unit 100, the non-power supply driving outdoor unit 200, and the indoor units 300 and 310 will be described.

  During the cooling operation, the power-driven outdoor unit four-way valve 114 and the non-power-driven outdoor unit four-way valve 214 are set so that the refrigerant flows through a solid line (see FIG. 2). The engine exhaust heat exchanger refrigerant flow rate adjustment valve 216 is closed, and no refrigerant flows into the engine exhaust heat exchanger 217. The heating communication pipe opening / closing valve 246 controls opening / closing according to the operating states of the power supply driven compressor 111 and the non-power supply driven compressor 211.

  The cooling load is smaller than the cooling capacity when the power-driven compressor 111 and the engine-driven compressor 211 are both operated at the minimum operating frequency (the minimum cooling capacity when both compressors are operating), and the power-driven compressor 111 and the engine When one of the drive compressors 211 is selected and operated, the heating suction communication pipe opening / closing valve 246 is closed.

  When the cooling load is larger than the minimum cooling capacity during the operation of both compressors and both the power supply driven compressor 111 and the engine driven compressor 211 are operating, for example, the outdoor fan 120 of the power supply outdoor unit 100 is used. So that the sum of the power consumption of the outdoor air blower 220 of the non-power-driven outdoor unit 200 and the non-power-driven outdoor unit 200 is minimized. The opening degree of the unit decompression device 115 and the opening degree of the non-power source driving outdoor unit decompression device 215 of the non-power source driving outdoor unit 200 are adjusted. If all the refrigerants sent out by the power-driven compressor 111 and the engine-driven compressor 211 are condensed in the outdoor heat exchanger 230 of the non-power-driven outdoor unit 200, that is, outdoor ventilation of the power-driven outdoor unit 100. If the sum of the power consumption of the outdoor fan 120 of the power source driven outdoor unit 100 and the power consumption of the outdoor fan 220 of the non-power source driven outdoor unit 200 is minimized when the fan 120 is stopped, suction during heating is performed. The connecting pipe opening / closing valve 246 is opened, the power drive outdoor unit decompression device 115 of the power drive outdoor unit 100 is closed, and the opening degree of the non-power drive outdoor unit decompression device 215 of the non-power drive outdoor unit 200 is opened.

  By doing so, all of the refrigerant delivered by the power supply driven compressor 111 flows through the outdoor unit heating-time suction communication pipe 241 to the outdoor heat exchanger 230 of the non-power supply driven outdoor unit 200.

On the other hand, during the heating operation, basically, the operation described in the first embodiment is performed. That is, the power drive outdoor unit decompression device 115 of the power drive outdoor unit 100 is fully closed or considerably closed, and the amount of refrigerant flowing in the outdoor heat exchanger 130 of the power drive outdoor unit 100 is determined by the non-power drive outdoor unit 200. , The amount of refrigerant flowing to the outdoor heat exchanger 230 and the amount of refrigerant flowing to the engine exhaust heat heat exchanger 217 are considerably smaller. In this way, all the refrigerant evaporates without excessively reducing the temperature of the refrigerant flowing through the outdoor heat exchanger 130. That is, moisture in the outside air hardly freezes on the fin surface of the outdoor heat exchanger 130, and frost formation hardly occurs.

  If frost formation occurs in the outdoor heat exchanger 130 of the power supply outdoor unit 100, the outdoor heat exchanger 130 of the power drive outdoor unit 100 needs to be defrosted. At this time, the power-driven outdoor unit four-way valve 114 and the non-power-driven outdoor unit four-way valve 214 are set so that the refrigerant flows through the solid line (the same setting as in the cooling operation), and the power-driven compressor 111 and the engine-driven compressor 211 are set. Are operated simultaneously. In the non-power source drive outdoor unit 200, the engine exhaust heat exchanger refrigerant flow rate adjustment valve 216 is closed, the non-power source drive outdoor unit decompression device 215 is closed, and the heating intake communication pipe opening / closing valve 246 is opened.

  By doing so, in addition to the high-temperature refrigerant discharged from the power supply-driven compressor 111, the high-temperature refrigerant discharged from the engine-driven compressor 211 also passes to the outdoor heat exchanger 130 through the outdoor unit heating communication pipe 241. Inflow.

  As apparent from the above description, in the present embodiment, during heating, a part of the refrigerant to be evaporated in the outdoor heat exchanger 130 of the power supply outdoor unit 100 is exchanged with the outdoor heat of the non-power supply outdoor unit 200. The evaporator 230 and the engine exhaust heat exchanger 217 evaporate. Note that the refrigerant evaporated in the outdoor heat exchanger 230 and the engine exhaust heat exchanger 217 is returned to the non-power source driven compressor 211 and the heating inlet communication pipe opening / closing valve 246 is opened, so that the outdoor unit intake heating communication is performed. It returns also to the power supply drive compressor 111 through the pipe | tube 241. FIG.

  Therefore, as in the first embodiment, during the heating operation, the amount of refrigerant flowing to the outdoor heat exchanger 130 of the power supply outdoor unit 110 is reduced, and the amount of heat exchange for evaporating the refrigerant is reduced. It is possible to prevent frost formation in the exchanger 130 and maintain the heating capacity.

  When the defrosting of the outdoor heat exchanger 130 of the power supply driven outdoor unit 110 is necessary, in addition to the power supply driven compressor 111, the high-temperature discharged refrigerant of the non-power supply driven compressor 211 is also heated during outdoor unit heating. The non-power supply driven outdoor unit pressure reducing device 215, the engine exhaust heat heat exchanger refrigerant flow rate adjustment valve 216, and the heating intake communication pipe opening / closing valve 246 are controlled so as to flow into the outdoor heat exchanger 130 through the intake communication pipe 241. . Therefore, the time required for defrosting the outdoor heat exchanger 130 can be shortened, and comfortable heating can be provided to the user.

  Further, by reducing or eliminating the heat exchange amount in the outdoor heat exchanger 130 of the power supply outdoor unit 110, the rotational speed of the outdoor fan 120 can be reduced or made zero. Therefore, it is possible to suppress the power consumption of the outdoor blower fan 120 and improve the efficiency of the entire air conditioner.

  At the time of cooling, according to the cooling load, the amount of refrigerant flowing to the outdoor heat exchanger 130 of the power supply driven outdoor unit 100 and the amount of refrigerant flowing to the outdoor heat exchanger 230 of the non-power supply driven outdoor unit 200 are set to the outdoor fan 120, 220. In order to minimize the total consumption energy, the heating communication pipe opening / closing valve 246 is opened, the opening degree of the power drive outdoor unit decompression device 115 of the power drive outdoor unit 100, and the non-power drive outdoor unit 200 non- The opening degree of the power supply outdoor unit decompression device 215 is adjusted.

  Therefore, even during the cooling operation, the power consumption of the outdoor fan 120 can be suppressed, and the efficiency of the entire air conditioner can be improved.

  INDUSTRIAL APPLICABILITY The present invention can be suitably used as an air conditioner capable of continuous operation while maintaining capacity during heating operation.

100 power-driven outdoor unit 111 power-driven compressor 115 power-driven outdoor unit decompressor 130 power-source outdoor unit outdoor heat exchanger 200 non-power-driven outdoor unit 211 non-power-driven compressor 215 non-power-driven outdoor unit decompressor 217 engine exhaust Thermal heat exchanger 230 Outdoor heat exchanger 240 for non-power source driven outdoor unit Intake communication pipe 245 between outdoor units Suction communication pipe on / off valves 300, 310 Indoor unit

Claims (5)

  At least one indoor unit includes a power supply outdoor unit equipped with a power supply driven compressor driven by electric power and a non-power supply outdoor unit equipped with a non-power supply driven compressor driven by a drive source other than electric power. In the air conditioner connected in parallel to the extending inter-unit piping, the power-driven outdoor unit suction pipe through which the refrigerant sucked by the power-driven compressor flows in the power-driven outdoor unit, and the non-power-driven drive in the non-power-driven outdoor unit An outdoor unit suction communication pipe connecting a non-power supply driven outdoor unit suction pipe through which a refrigerant sucked by the compressor flows is provided, and the power supply drive outdoor unit suction pipe and the non-power supply drive room are provided in the middle of the outdoor unit suction communication pipe. An air conditioner comprising a first on-off valve that controls communication with a unit suction pipe.   2. The air conditioner according to claim 1, wherein an amount of refrigerant flowing from the indoor unit into the outdoor heat exchanger of the power supply outdoor unit is reduced during heating operation, and an amount of refrigerant flowing into the outdoor heat exchanger of the non-power supply outdoor unit is reduced. In addition, the first on-off valve is opened to allow a part of the refrigerant discharged from the outdoor heat exchanger of the non-power-driven outdoor unit to flow to the power-driven compressor of the power-driven outdoor unit. The air conditioner according to claim 1.   From at least one indoor unit, a power-driven outdoor unit equipped with a power-driven compressor driven by electric power and a non-power-driven outdoor unit equipped with a non-power-driven compressor driven by a driving source other than electric power In the air conditioner connected in parallel to the extending inter-unit piping, the power-driven outdoor unit discharge pipe through which the refrigerant discharged from the power-driven compressor flows in the power-driven outdoor unit, and the non-power-driven drive in the non-power-driven outdoor unit An outdoor unit discharge communication pipe connecting a non-power supply outdoor unit discharge pipe through which refrigerant discharged from the compressor flows is provided, and the power supply drive outdoor unit discharge pipe and the non-power supply drive room are provided in the middle of the outdoor unit discharge communication pipe. An air conditioner comprising a second on-off valve that controls communication with a unit discharge pipe.   4. The air conditioner according to claim 3, wherein a part of the refrigerant discharged from the compressor of the non-power-driven outdoor unit by opening the second on-off valve upon defrosting the outdoor heat exchanger of the power-driven outdoor unit. The air conditioner according to claim 1, wherein the air is passed through an outdoor heat exchanger of the power supply outdoor unit. 5. The air conditioner according to claim 1, wherein an excluded volume of the non-power source driven compressor is larger than an excluded volume of the power source driven compressor.