WO2014054090A1

WO2014054090A1 - Air conditioning device

Info

Publication number: WO2014054090A1
Application number: PCT/JP2012/075309
Authority: WO
Inventors: 博文 ▲高▼下
Original assignee: 三菱電機株式会社
Priority date: 2012-10-01
Filing date: 2012-10-01
Publication date: 2014-04-10
Also published as: US20150219373A1; EP2905560A1; EP2905560A4; JPWO2014054090A1

Abstract

An air conditioning device (1) comprising: a compressor (101); a heat source machine-side heat exchanger (103); a plurality of usage-side heat exchangers (105); and a relay machine (B) that switches some of the plurality of usage-side heat exchangers (105) to a cooling operation side and switches some of the plurality of usage-side heat exchangers (105) to a heating operation side. The air conditioning device (1) performs simultaneous cooling and heating operations by switching each of the plurality of usage-side heat exchangers (105) among the plurality of usage-side heat exchangers (105) to either the cooling operation side or the heating operation side, in accordance with a control command. The air conditioning device (1) comprises: a second flow rate control device (122) that adjusts the flow rate for coolant that flows into the compressor (101); a third flow rate control device (123) connected in parallel with the third flow rate control device (123) and which adjusts the flow rate of coolant that flows into the heat source machine-side heat exchanger (103); and a control unit (141) that adjusts the second flow rate control device (122) and the third flow rate control device (123). The control unit (141) adjusts the degree of opening of the second flow rate control device (122) and the degree of opening of the third flow rate control device (123), in accordance with the outside air temperature.

Description

Air conditioner

The present invention relates to an air conditioner.

Some conventional air conditioners include a high-stage compressor and a low-stage compressor, and liquid refrigerant is allowed to flow from the injection pipe to the high-stage compressor (see, for example, Patent Document 1). In addition, the conventional air conditioner includes a flow control device between the heat source side heat exchanger and the pressure detection means, and controls the opening degree of the flow control device according to the detection value of the pressure detection means. (For example, see Patent Document 1).

Japanese Patent No. 4675810 (paragraph [0018])

However, in the conventional air conditioner (Patent Document 1), when the outside air temperature decreases during the simultaneous cooling and heating operation, a plurality of compressors must be provided in order to maintain the heating capacity. In order to continue the operation, the opening degree of the flow control device has to be controlled based on the pressure detection means.
Therefore, when the outside air temperature decreases during the simultaneous cooling and heating operation, a high-cost air conditioner is required to continue the cooling operation while maintaining the heating capacity.
For this reason, the conventional air conditioner (Patent Document 1) has a problem that, when the outside air temperature decreases during the cooling and heating simultaneous operation, the cooling operation cannot be continued while maintaining the heating capacity at low cost. there were.

The present invention has been made to solve the above-described problems. Even when the outside air temperature decreases during the simultaneous cooling and heating operation, the cooling operation can be performed while maintaining the heating capacity at a low cost. It aims at providing the air conditioning apparatus which can be continued.

The present invention performs heat exchange between one compressor that compresses and discharges the refrigerant, a heat source side heat exchanger that exchanges heat between the refrigerant and the surrounding heat source medium, and the refrigerant and the surrounding utilization medium. Provided between a plurality of use side heat exchangers, the heat source unit side heat exchanger, and the use side heat exchanger, and switching a part of the plurality of use side heat exchangers to a cooling operation side, A relay that switches a part of the plurality of use side heat exchangers to the heating operation side, and according to a control command, any one of the cooling operation side and the heating operation side among the plurality of use side heat exchangers An air conditioner that performs simultaneous cooling and heating operations by switching each of the plurality of use side heat exchangers, provided between the relay unit and the heat source unit side heat exchanger, the heat source Bypass the refrigerant flowing into the machine side heat exchanger and supply it to the one compressor An injection pipe, a flow control device for a compressor that is provided in the injection pipe and adjusts a flow rate of the refrigerant flowing into the one compressor, and is connected in parallel to the flow control device for the compressor, A heat source side heat exchanger flow control device that adjusts the flow rate of the refrigerant flowing into the heat source side heat exchanger, a control unit that adjusts the compressor flow control device and the heat source side heat exchanger flow control device The control unit is an air conditioner that adjusts the opening of the compressor flow control device and the opening of the heat source unit heat exchanger flow control device according to the outside air temperature.

In the case where the outside air temperature decreases during simultaneous cooling and heating operation by suppressing the refrigerant flow rate to the heat source side heat exchanger while increasing the injection amount to one compressor according to the outside air temperature. Even so, the cooling operation can be continued at low cost while maintaining the heating capacity. Due to this configuration, there is an effect that high-efficiency simultaneous cooling and heating operation can be performed.

It is a figure which shows the structural example of the air conditioning apparatus 1 in Embodiment 1 of this invention. It is the figure which modeled and showed the connection relation of the 2nd flow control device 122 in Embodiment 1 of the present invention, the 3rd flow control device 123, and the 3rd flow regulator 115 of relay machine B. It is a cooling-heating simultaneous operation in Embodiment 1 of this invention, Comprising: It is a figure which shows the structural example of the air conditioning apparatus 1 explaining the driving | running state in the case of a cooling main body. It is a cooling-heating simultaneous operation in Embodiment 1 of this invention, Comprising: It is a figure which shows the structural example of the air conditioning apparatus 1 explaining the driving | running state in the case of heating main. It is a figure explaining an example of the correlation with the outside temperature according to the opening degree of the 2nd flow control apparatus 122 in Embodiment 1 of this invention, and a heating capability ratio. It is a figure explaining an example of the correlation of the outside temperature according to the opening degree of the 2nd flow control apparatus 122 in Embodiment 1 of this invention, and the opening degree of the 3rd flow control apparatus 123, and a flow rate ratio. The outside air temperature and the flow rate ratio according to the opening of the second flow control device 122, the opening of the third flow control device 123, and the opening of the third flow regulator 115 in Embodiment 1 of the present invention It is a figure explaining an example of correlation of these. It is a figure explaining an example of the correlation of the outside temperature and the heating capability ratio according to the case where there is the case where there is appropriate control of the 2nd flow control device 122 in Embodiment 1 of the present invention. It is a figure explaining an example of the correlation of the outside temperature and the heating capacity ratio according to the case where there is no proper control of the 4th flow regulating valve 124 in Embodiment 1 of the present invention. It is a flowchart explaining the operation example of the control part 141 with which the heat-source equipment A in Embodiment 1 of this invention is provided. It is a flowchart explaining the operation example of the control part 151 with which the repeater B in Embodiment 1 of this invention is provided.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

Embodiment 1 FIG.
FIG. 1 is a diagram illustrating a configuration example of an air-conditioning apparatus 1 according to Embodiment 1 of the present invention. As shown in FIG. 1, the air conditioner 1 uses an indoor unit C, an indoor unit D, a relay unit B, check valves 118 to 121, a four-way valve 102, and the like. A cycle and a heating refrigeration cycle are formed, and simultaneous cooling and heating operations are performed. When the outside air temperature decreases during the simultaneous cooling and heating operation, as will be described in detail later, the amount of refrigerant flowing to the compressor 101 is adjusted by the second flow control device and the amount of refrigerant flowing to the heat source unit side heat exchanger 103 is described later. Is adjusted by the third flow control device 123. With this operation, among the refrigerant amount flowing from the relay B to the heat source device A, the refrigerant amount flowing to the compressor 101 and the refrigerant amount flowing to the heat source device side heat exchanger 103 are distributed. As a result, even when the outside air temperature decreases during the simultaneous cooling and heating operation, the cooling operation is continued while maintaining the heating capacity at a low cost, and the highly efficient simultaneous cooling and heating operation is performed.
Hereinafter, details of the above-described contents will be described in order.

The air conditioner 1 includes a heat source unit A, a relay unit B, an indoor unit C, an indoor unit D, and the like. The relay unit B is provided between the heat source unit A, the indoor unit C, and the indoor unit D. The heat source machine A and the relay machine B are connected by a first connection pipe 106 and a second connection pipe 107 having a pipe diameter smaller than that of the first connection pipe 106. Moreover, the relay machine B and the indoor unit C are connected by the 1st connection piping 106c and the 2nd connection piping 107c. Moreover, the relay machine B and the indoor unit D are connected by the 1st connection piping 106d and the 2nd connection piping 107d.
With this connection configuration, the relay unit B relays the refrigerant flowing between the heat source unit A, the indoor unit C, and the indoor unit D.
In addition, although an example in case of one heat source unit and two indoor units will be described, the present invention is not particularly limited thereto. For example, the case where two or more indoor units are provided may be used. Further, for example, a plurality of heat source machines may be used. Further, for example, a plurality of relay machines B may be provided.

The heat source machine A includes a compressor 101, a four-way valve 102, a heat source machine side heat exchanger 103, and an accumulator 104. The heat source machine A includes a check valve 118, a check valve 119, a check valve 120, and a check valve 121. Further, the heat source machine A includes a second flow rate control device 122, a third flow rate control device 123, a fourth flow rate adjustment valve 124, and a control unit 141. Further, the heat source device A includes an outside air temperature detecting unit 131 that measures the outside air temperature and supplies the measurement result to the control unit 141.

The compressor 101 is provided between the four-way valve 102, the accumulator 104 and the second flow control device 122. The compressor 101 compresses and discharges the refrigerant. The discharge side is connected to the four-way valve 102 and the suction side is connected to the accumulator 104 and the second flow control device 122.

The four-way valve 102 includes four ports. Each port includes a discharge side of the compressor 101, a heat source unit side heat exchanger 103, an accumulator 104, an outlet side of the check valve 119, and an inlet of the check valve 120. And the refrigerant flow path is switched.

The heat source machine side heat exchanger 103 is provided between the four-way valve 102, the third flow rate control device 123, and the fourth flow rate adjustment valve 124. One of the heat source device side heat exchangers 103 is connected to the four-way valve 102 and the other is connected to a pipe connected to the third flow rate control device 123 and the fourth flow rate adjustment valve 124. The heat source device side heat exchanger 103 exchanges heat between the refrigerant flowing in the heat source device side heat exchanger 103 and the ambient air of the heat source device side heat exchanger 103.

The accumulator 104 is connected between the four-way valve 102 and the suction side of the compressor 101, separates the liquid refrigerant, and supplies the gas refrigerant to the compressor 101.

The compressor 101, the four-way valve 102, and the heat source device side heat exchanger 103 described above constitute a part of the refrigerant circuit.

The check valve 118 includes an outlet side of the fourth flow rate adjustment valve 124 and the check valve 121 connected to the heat source apparatus side heat exchanger 103, and an outlet side of the second connection pipe 107 and the check valve 120. Between. The inlet side of the check valve 118 is connected to piping connected to the fourth flow rate adjustment valve 124 and the outlet side of the check valve 121. The outlet side of the check valve 118 is connected to the second connection pipe 107 and a pipe connected to the outlet side of the check valve 120. The check valve 118 allows the refrigerant to flow only from one direction to the second connection pipe 107 through the fourth flow rate adjustment valve 124 from the heat source apparatus side heat exchanger 103.

The check valve 119 is provided between the inlet side of the four-way valve 102 and the check valve 120 and the inlet side of the first connection pipe 106 and the check valve 121. The inlet side of the check valve 119 is connected to a pipe connected to the first connection pipe 106 and the inlet side of the check valve 121. The outlet side of the check valve 119 is connected to a pipe connected to the four-way valve 102 and the inlet side of the check valve 120. The check valve 119 allows the refrigerant to flow only from one direction from the first connection pipe 106 to the four-way valve 102.

The check valve 120 is provided between the outlet side of the four-way valve 102 and the check valve 119, the outlet side of the check valve 118, and the second connection pipe 107. The inlet side of the check valve 120 is connected to piping connected to the four-way valve 102 and the outlet side of the check valve 119. The outlet side of the check valve 120 is connected to a pipe connected to the outlet side of the check valve 118 and the second connection pipe 107. The check valve 120 allows the refrigerant to flow from the four-way valve 102 to the second connection pipe 107 only from one direction.

The check valve 121 includes an inlet side of the check valve 119 and the first connection pipe 106, and a fourth flow rate adjustment valve 124 connected to the inlet side of the check valve 118 and the heat source unit side heat exchanger 103. Between. The inlet side of the check valve 121 is connected to a pipe connected to the inlet side of the check valve 119 and the first connection pipe 106. The outlet side of the check valve 121 is connected to a pipe connected to the inlet side of the check valve 118 and the fourth flow rate adjustment valve 124. The check valve 121 allows the refrigerant to flow only from one direction from the first connection pipe 106 to the heat source apparatus side heat exchanger 103 via the fourth flow rate adjustment valve 124.

The check valve 118 to the check valve 121 described above constitute a flow path switching valve of the refrigerant circuit. During the cooling and heating simultaneous operation of the flow path switching valve, the relay unit B, which will be described in detail later, the indoor unit C, and the indoor unit D, in the refrigerant circuit, the refrigeration cycle of the cooling operation, and the heating operation A refrigeration cycle is formed.

The second flow control device 122 has one end connected to the inlet side of the check valve 121 and the other end connected to the suction side of the compressor 101. The inlet side of the check valve 121 is connected to one end of the first connection pipe 106. The other end of the first connection pipe 106 is connected to the repeater B.
Due to this connection configuration, the second flow control device 122 is connected in series with the relay machine B, and the refrigerant is supplied from the relay machine B. The second flow control device 122 is a flow control device having a variable opening.
Therefore, the second flow control device 122 controls the refrigerant amount after gas-liquid separation flowing in from the relay B by adjusting the opening, and the refrigerant is controlled while the refrigerant amount is controlled. To supply.
The second flow rate control device 122 corresponds to the compressor flow rate control device in the present invention.

The third flow rate control device 123 is provided between the second flow rate control device 122 and the heat source unit side heat exchanger 103 and is connected in parallel with the second flow rate control device 122. Specifically, the third flow control device 123 is connected to the end of the second flow control device 122 on the side connected to the inlet side of the check valve 121 among the both ends of the second flow control device 122. Connected with the part.
Due to this connection configuration, the third flow control device 123 is connected in series with the relay unit B, and the refrigerant is supplied from the relay unit B. The third flow control device 123 is a flow control device having a variable opening.
Therefore, the third flow control device 123 controls the amount of refrigerant flowing from the relay B by adjusting the opening, and supplies the refrigerant to the heat source device side heat exchanger 103 in a state where the amount of refrigerant is controlled.
The third flow rate control device 123 corresponds to the heat source unit side heat exchanger flow rate control device in the present invention.

Further, because of the connection configuration described above, the third flow rate control device 123 is connected in parallel with the second flow rate control device 122 and connected in series with the repeater B.
Therefore, the refrigerant flowing from the relay B is the second flow control device 122 and the third flow rate according to the opening of the second flow control device 122 and the opening of the third flow control device 123. It is distributed and supplied to the control device 123.

The fourth flow rate adjusting valve 124 is provided between the outlet side of the check valve 121 and the inlet side of the check valve 118 and the heat source unit side heat exchanger 103, and in parallel with the third flow rate control device 123. Connected. Specifically, one end of the fourth flow rate adjustment valve 124 is connected to a pipe connected to the outlet side of the check valve 121 and the inlet side of the check valve 118. The other end of the fourth flow rate adjustment valve 124 is connected to piping on the side connected to the heat source device side heat exchanger 103 in both ends of the third flow rate control device 123.
Due to this connection configuration, the fourth flow rate adjustment valve 124 is connected in series via the relay B and the check valve 121, and the refrigerant is supplied from the relay B. The fourth flow rate adjustment valve 124 is a flow rate adjustment valve having a variable opening degree.
Therefore, the fourth flow rate adjustment valve 124 controls the amount of refrigerant flowing from the relay B by adjusting the opening, and supplies the refrigerant to the heat source device side heat exchanger 103 in a state where the amount of refrigerant is controlled.

Due to such a connection configuration, the fourth flow rate adjustment valve 124 is connected in parallel to the second flow rate control device 122 and the third flow rate control device 123 via the check valve 121 and is connected in series with the relay B. Connected.
Therefore, the refrigerant flowing from the relay machine B depends on the opening of the second flow control device 122, the opening of the third flow control device 123, and the opening of the fourth flow control valve 124. The second flow control device 122, the third flow control device 123, and the fourth flow control valve 124 are distributed and supplied.

The control unit 141 is configured mainly by, for example, a microprocessor unit, and performs overall control of the entire heat source apparatus A, communication with an external device, for example, the relay machine B, and various calculations.

The outside air temperature detection means 131 is formed by a thermistor, for example. The outside air temperature detection means 131 supplies the outside air temperature measurement result to the control unit 141. The outside air temperature detection means 131 may supply the measurement result to the control unit 141 as it is, or may supply the measurement result accumulated after accumulating the measurement result for a certain period to the control unit 141 at a predetermined cycle interval.
In the above description, the example in which the outside temperature detecting means 131 is a thermistor has been described. However, the present invention is not particularly limited to this.

The relay B includes a first branching unit 110, a second branching unit 111, a gas-liquid separator 112, a second flow rate regulator 113, a third flow rate regulator 115, a first heat exchanger 116, a first 2 heat exchanger 117, temperature detection means 125, pressure detection means 127a, pressure detection means 127b, and control unit 151.
The relay machine B is connected to the heat source machine A via the first connection pipe 106 and the second connection pipe 107. The relay machine B is connected to the indoor unit C via the first connection pipe 106c and the second connection pipe 107c. The relay machine B is connected to the indoor unit D through the first connection pipe 106d and the second connection pipe 107d.

The first branching unit 110 includes an electromagnetic valve 108a and an electromagnetic valve 108b. The solenoid valve 108a and the solenoid valve 108b are connected to the indoor unit C through the first connection pipe 106c. The solenoid valve 108a and the solenoid valve 108b are connected to the indoor unit D through the first connection pipe 106d.
The solenoid valve 108a is a valve that can be opened and closed, and has one end connected to the first connection pipe 106 and the other end connected to one terminal of the first connection pipe 106c, the first connection pipe 106d, and the solenoid valve 108b. It is connected. The electromagnetic valve 108b is a valve that can be opened and closed, and has one end connected to the second connection pipe 107 and the other end connected to one terminal of the first connection pipe 106c, the first connection pipe 106d, and the electromagnetic valve 108a. It is connected.

The first branch 110 is connected to the indoor unit C via the first connection pipe 106c. The first branch 110 is connected to the indoor unit D via the first connection pipe 106d. The first branch part 110 is connected to the heat source machine A through the first connection pipe 106 and the second connection pipe 107. The first branching section 110 is connected to one of the first connection pipe 106 c, the first connection pipe 106, and the second connection pipe 107 using the electromagnetic valve 108 a and the electromagnetic valve 108 b. The first branch part 110 is connected to one of the first connection pipe 106d, the first connection pipe 106, and the second connection pipe 107 using the electromagnetic valve 108a and the electromagnetic valve 108b.

The second branch portion 111 includes a check valve 137a and a check valve 137b. The check valve 137a and the check valve 137b are connected to each other in an antiparallel relationship. The input side of the check valve 137a and the output side of the check valve 137b are connected to the indoor unit C through the second connection pipe 107c, and are connected to the indoor unit D through the second connection pipe 107d. . The output side of the check valve 137a is connected to the meeting part 137a_all. The input side of the check valve 137b is connected to the meeting part 137b_all.

The second branch portion 111 is connected to the indoor unit C via the second connection pipe 107c. The second branch portion 111 is connected to the indoor unit D via the second connection pipe 107d. The second branch part 111 is connected to the second flow rate regulator 113 and the first heat exchanger 116 via the meeting part 137a_all. The second branch part 111 is connected to the third flow rate regulator 115 and the first heat exchanger 116 via the meeting part 137b_all.

The gas-liquid separator 112 is provided in the middle of the second connection pipe 107, the gas phase portion is connected to the electromagnetic valve 108b of the first branching portion 110, and the liquid phase portion is the first heat exchange. The second branching unit 111 is connected to the second branching unit 111 through the second unit 116, the second flow rate regulator 113, the second heat exchanger 117, and the third flow rate regulator 115.

The second flow rate regulator 113 has one end connected to the first heat exchanger 116 and the other end connected to one end of the second heat exchanger 117 and the meeting part 137a_all of the second branching part 111. . The piping connected between the first heat exchanger 116 and the second flow rate regulator 113 is provided with a pressure detection means 127a described later in detail. A pipe connected between the second flow rate regulator 113, the second heat exchanger 117, and the meeting portion 137a_all is provided with a pressure detection means 127b described later in detail.
The second flow rate regulator 113 is a flow rate regulator whose opening degree can be adjusted so that the difference between the pressure value detected by the pressure detection means 127a and the pressure value detected by the pressure detection means 127b is constant. Adjust the opening.

One end of the third flow rate regulator 115 is connected to the bypass pipe 114 side of the second heat exchanger 117, and the other end is connected to the pipe side connecting the meeting part 137 b_all and the second heat exchanger 117. The The third flow rate regulator 115 is a flow rate regulator whose opening degree can be adjusted, and is any one or a plurality of the outside air temperature detection means 131, the temperature detection means 125, the pressure detection means 127a, and the pressure detection means 127b. Adjust the opening by the combination.
The bypass pipe 114 has one end connected to the first connection pipe 106 and the other end connected to the third flow rate regulator 115.
Therefore, the amount of refrigerant supplied to the heat source unit A varies depending on the opening of the third flow rate regulator 115.

The first heat exchanger 116 is provided between the gas-liquid separator 112, the second heat exchanger 117, and the second flow rate regulator 113, and includes a bypass pipe 114, the gas-liquid separator 112, and the first heat exchanger 116. Heat exchange is performed with a pipe provided between the two flow rate regulators 113.

The second heat exchanger 117 is between the first heat exchanger 116 and the second flow rate regulator 113, and one end of the third flow rate regulator 115 and the other end of the third flow rate regulator 115. Is provided. In this case, the other end of the third flow rate regulator 115 is connected to the meeting part 137b_all. The second heat exchanger 117 performs heat exchange between the bypass pipe 114 and a pipe provided between the second flow rate regulator 113 and the third flow rate regulator 115.

The temperature detection means 125 is formed by a thermistor, for example. The temperature detection means 125 measures the temperature of the refrigerant flowing in the pipe provided between the third flow rate regulator 115 and the second heat exchanger 117 and supplies the measurement result to the control unit 151. The temperature detection unit 125 may supply the measurement result to the control unit 151 as it is, or may supply the measurement result accumulated after a certain period of accumulation to the control unit 151 at a predetermined cycle interval.
In the above description, the temperature detection unit 125 is described as an example of a thermistor, but is not particularly limited thereto.

The pressure detection unit 127 a measures the pressure of the refrigerant flowing in the pipe provided between the first heat exchanger 116 and the second flow rate regulator 113 and supplies the measurement result to the control unit 151.
The pressure detection means 127b measures the pressure of the refrigerant flowing in the pipe provided between the second flow rate regulator 113, the second heat exchanger 117, and the second branch part 111, and the measurement result is obtained. It supplies to the control part 151.
The pressure detection means 127a and the pressure detection means 127b are collectively referred to as a pressure detection means 127. The pressure detection unit 127 may supply the measurement result as it is to the control unit 151, or may supply the measurement result accumulated after a certain period of accumulation to the control unit 151 at a predetermined cycle interval.

The control unit 151 is configured mainly by, for example, a microprocessor unit, and executes overall control of the entire relay unit B, communication with an external device, for example, the heat source unit A, and various calculations.

The indoor unit C includes a use side heat exchanger 105c, a liquid pipe temperature detecting means 126c, a first flow rate regulator 109c, and the like. A plurality of use side heat exchangers 105c are provided. Between the use side heat exchanger 105c and the first flow rate regulator 109c, a liquid pipe temperature detecting means 126c for detecting the temperature of the pipe is provided.
The utilization side heat exchanger 105c and the first flow rate regulator 109c described above constitute a part of the refrigerant circuit.

The indoor unit D includes a use side heat exchanger 105d, a liquid pipe temperature detection means 126d, a first flow rate regulator 109d, and the like. A plurality of use side heat exchangers 105d are provided. Between the use side heat exchanger 105d and the first flow rate regulator 109d, a liquid pipe temperature detecting means 126d for detecting the temperature of the pipe is provided.
The utilization side heat exchanger 105d and the first flow rate control device 109d described above constitute a part of the refrigerant circuit.

FIG. 2 is a diagram showing a modeled connection relationship between the second flow rate control device 122, the third flow rate control device 123, and the third flow rate regulator 115 of the relay B in the first embodiment of the present invention. It is. As shown in FIG. 2, a second flow rate control device 122 is provided between the relay machine B and the compressor 101. In addition, a third flow rate control device 123 and a fourth flow rate adjustment valve 124 are provided between the relay unit B and the heat source unit side heat exchanger 103. The third flow control device 123 and the fourth flow control valve 124 are connected in parallel, and the third flow control device 123 and the second flow control device 122 are connected in parallel. Therefore, the 2nd flow control device 122, the 3rd flow control device 123, and the 4th flow control valve 124 have a parallel relation mutually, and have a serial relation to relay machine B.
As described above, the relay unit B includes the third flow rate regulator 115 and adjusts the amount of refrigerant to the heat source unit A side.

Therefore, the third flow rate regulator 115 determines the amount of refrigerant flowing through the second flow rate control device 122, the third flow rate control device 123, and the fourth flow rate adjustment valve 124.
Note that the control unit 141 adjusts the opening degrees of the second flow rate control device 122, the third flow rate control device 123, and the fourth flow rate adjustment valve 124. The control unit 151 adjusts the opening degree of the third flow rate regulator 115. And the control part 141 and the control part 151 supply mutual control content by transmitting / receiving various signals.

FIG. 3 is a diagram illustrating a configuration example of the air-conditioning apparatus 1 for explaining an operation state in the cooling-heating simultaneous operation according to the first embodiment of the present invention and mainly in a cooling operation.
As a precondition, it is assumed that a cooling operation is set for the indoor unit C and a heating operation is set for the indoor unit D, and the operation of the air conditioner 1 is performed mainly by the cooling.

Of the electromagnetic valve 108a, the indoor unit C side is opened, and the indoor unit D side is closed. Of the electromagnetic valve 108b, the indoor unit C side is closed and the indoor unit D side is opened.
The opening degree of the second flow rate regulator 113 is controlled so that the differential pressure between the pressure detection means 127a and the pressure detection means 127b becomes an appropriate value.

The flow of the refrigerant will be described. As indicated by a solid thick arrow, the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 101 flows into the heat source unit side heat exchanger 103 through the four-way valve 102.
The heat source machine side heat exchanger 103 exchanges heat with a heat source medium such as air or water. The heat-exchanged high-temperature and high-pressure gas refrigerant becomes a gas-liquid two-phase high-temperature and high-pressure refrigerant. Next, the gas-liquid two-phase high-temperature and high-pressure refrigerant passes through the second connection pipe 107 via the fourth flow rate adjustment valve 124 and the check valve 118 and is supplied to the gas-liquid separator 112 of the relay B. Is done.
The gas-liquid separator 112 separates the gas-liquid two-phase high-temperature and high-pressure refrigerant into a gaseous refrigerant and a liquid refrigerant.
The separated gaseous refrigerant flows into the first branch part 110. The gaseous refrigerant that has flowed into the first branch portion 110 is supplied to the indoor unit D in which the heating operation is set, through the electromagnetic valve 108b on the open side and the first connection pipe 106d.

In the indoor unit D, the use side heat exchanger 105d exchanges heat with a use medium such as air, and condenses and liquefies the supplied gaseous refrigerant.
In addition, the usage-side heat exchanger 105d is controlled by the first flow rate regulator 109d based on the degree of supercooling at the outlet of the usage-side heat exchanger 105d.
The first flow controller 109d depressurizes the liquid refrigerant condensed and liquefied by the use side heat exchanger 105d, and converts it into a gas-liquid two-phase refrigerant having an intermediate pressure that is an intermediate pressure between the high pressure and the low pressure.
The gas-liquid two-phase refrigerant that has reached the intermediate pressure flows into the second branch portion 111.
The gas refrigerant of the gas-liquid two-phase refrigerant that has flowed into the second branch portion 111 flows into the indoor unit D. The liquid refrigerant of the gas-liquid two-phase refrigerant that has flowed into the second branch part 111 exits from the second branch part 111, and then merges with the liquid refrigerant that has passed through the second flow rate regulator 113, so that the first heat After the heat exchange is performed by the exchanger 116 as described later, the flow returns to the second branch portion 111 again and flows into the indoor unit C and the indoor unit D.

At this time, the first connection pipe 106 has a low pressure, and the second connection pipe 107 has a high pressure. Therefore, due to the pressure difference between them, the refrigerant flows to the check valve 118 and the check valve 119, while the refrigerant does not flow to the check valve 120 and the check valve 121.

On the other hand, the liquid refrigerant separated by the gas-liquid separator 112 passes through the second flow rate regulator 113 that controls the pressure difference between the high pressure and the intermediate pressure to be constant, and flows into the second branch portion 111. To do.
Next, in the second branch portion 111, the supplied liquid refrigerant passes through the check valve 108d connected to the indoor unit C and flows into the indoor unit C.
Next, the inflowing liquid refrigerant is decompressed to a low pressure by using the first flow rate regulator 109c controlled according to the degree of superheat at the outlet of the utilization side heat exchanger 105c of the indoor unit C. It is supplied to the heat exchanger 105c.
In the use-side heat exchanger 105c, the supplied liquid refrigerant is evaporated and gasified by exchanging heat with a use medium such as air.
The refrigerant that has been gasified to become a gas refrigerant passes through the first connection pipe 106 c and flows into the first branch 110. In the first branch part 110, the solenoid valve 108a on the side connected to the indoor unit C is open. Therefore, the gas refrigerant that has flowed in passes through the electromagnetic valve 108 a on the side connected to the indoor unit C, and flows into the first connection pipe 106.
Next, the gas refrigerant flows into the check valve 119 having a lower pressure than the check valve 121, and is sucked into the compressor 101 through the four-way valve 102 and the accumulator 104.
With such an operation, a refrigeration cycle is formed and a cooling main operation is performed.

In addition, among the refrigerants that have been separated by the gas-liquid separator 112 and have flowed into the second branch portion 111, there are refrigerants that have not flowed into the indoor unit C. Such a liquid refrigerant flows into the second branch portion 111, but flows into the third flow rate regulator 115 through the first heat exchanger 116. The third flow rate regulator 115 depressurizes the inflowing liquid refrigerant to a low pressure to lower the refrigerant evaporation temperature. In the first heat exchanger 116, the liquid refrigerant whose evaporation temperature has decreased passes through the bypass pipe 114, and exchanges heat with the liquid refrigerant mainly supplied from the second flow rate regulator 113. In the second heat exchanger 117, the liquid refrigerant supplied from the gas-liquid separator 112 becomes a gas refrigerant and flows into the first connection pipe 106.

FIG. 4 is a diagram showing a configuration example of the air-conditioning apparatus 1 for explaining an operation state in the case of heating and cooling simultaneous operation in Embodiment 1 of the present invention and mainly heating.
As a precondition, it is assumed that a heating operation is set for the indoor unit C and a cooling operation is set for the indoor unit D, and the operation of the air conditioner 1 is performed mainly by heating.

Of the electromagnetic valve 108a, the indoor unit C side is closed and the indoor unit D side is opened. Of the electromagnetic valve 108b, the indoor unit C side is opened, and the indoor unit D side is closed.
The opening degree of the second flow rate regulator 113 is controlled so that the differential pressure between the pressure detection means 127a and the pressure detection means 127b becomes an appropriate value.

The flow of the refrigerant will be described. As indicated by a solid thick arrow, the high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 101 passes through the four-way valve 102, the check valve 120, the second connection pipe 107, and the relay machine. B gas-liquid separator 112 is supplied.
The gas-liquid separator 112 supplies a high-temperature and high-pressure gas refrigerant to the first branch part 110. The gas refrigerant supplied to the first branch part 110 is supplied to the indoor unit C in which the heating operation is set, through the open solenoid valve 108b and the first connection pipe 106c.

In the indoor unit C, the use side heat exchanger 105c exchanges heat with a use medium such as air, and the supplied gas refrigerant is condensed and liquefied.
The use side heat exchanger 105c is controlled by the first flow rate regulator 109c based on the degree of supercooling at the outlet of the use side heat exchanger 105c.
The first flow controller 109c depressurizes the liquid refrigerant condensed and liquefied by the use side heat exchanger 105c, and converts it into a gas-liquid two-phase refrigerant having an intermediate pressure that is an intermediate pressure between the high pressure and the low pressure.
The gas-liquid two-phase refrigerant that has reached the intermediate pressure flows into the second branch portion 111.

Next, the gas-liquid two-phase refrigerant that has flowed into the second branch part 111 joins at the meeting part 137a_all. The gas-liquid two-phase refrigerant joined at the meeting part 137a_all passes through the first heat exchanger 116 to become a liquid refrigerant, reaches the meeting part 137b_all, passes through the check valve 137b connected to the indoor unit D, and passes through the second heat exchanger 116. It flows into the indoor unit D through the connecting pipe 107d.
Next, the inflowing liquid refrigerant is decompressed to a low pressure by using the first flow rate regulator 109d controlled according to the degree of superheat at the outlet of the utilization side heat exchanger 105d of the indoor unit D. It is supplied to the heat exchanger 105d.
In the use side heat exchanger 105d, the supplied liquid refrigerant evaporates and gasifies by exchanging heat with a use medium such as air.

The refrigerant that has been gasified to become a gas refrigerant passes through the first connection pipe 106d and flows into the first branch 110. In the 1st branch part 110, the solenoid valve 108a by the side connected with the indoor unit D is opening. Therefore, the gas refrigerant that has flowed in passes through the electromagnetic valve 108 a on the side connected to the indoor unit D, and flows into the first connection pipe 106.
Next, the gas refrigerant flows into the check valve 121 side having a pressure lower than that of the check valve 119, and flows into the fourth flow rate adjustment valve 124 and the heat source unit side heat exchanger 103 to evaporate into a gas state. . Next, the air is sucked into the compressor 101 through the four-way valve 102 and the accumulator 104.
With such an operation, a refrigeration cycle is formed, and a heating main operation is performed.

At this time, the first connection pipe 106 has a low pressure, and the second connection pipe 107 has a high pressure. Therefore, due to the pressure difference between them, the refrigerant flows to the check valve 120 and the check valve 121, while the refrigerant does not flow to the check valve 118 and the check valve 119.

Here, when the cooling / heating simultaneous operation is being performed and the outside air temperature is low during the heating-main operation, the heat source apparatus side heat exchanger 103, the second flow control device 122, the third flow control device 123, Are mutually influential.
Specifically, as the outside air temperature decreases, the air conditioner 1 cannot maintain a high pressure at a high level, and the heating capacity decreases. Moreover, since the low-pressure pressure decreases, the indoor unit D that is performing the cooling operation cannot maintain the continuous operation, and a problem occurs in both the cooling operation and the heating operation.

FIG. 5 is a diagram for explaining an example of the correlation between the outside air temperature and the heating capacity ratio according to the opening degree of the second flow control device 122 according to Embodiment 1 of the present invention.
In FIG. 5, it is assumed that the reference temperature on the horizontal axis is α and the reference heating capacity ratio on the vertical axis is β.
As shown in FIG. 5, when the outside air temperature falls below a certain value, if the opening of the second flow control device 122 is small, the heating capacity ratio is low, but the opening of the second flow control device 122 is reduced. If it is increased, the heating capacity ratio is improved.
In other words, in order to increase the heating capacity, the high pressure can be maintained high by increasing the opening of the second flow control device 122.
Specifically, by increasing the flow rate bypassed from the second flow control device 122 to the compressor 101, that is, the injection amount, the high-pressure pressure increases and the heating capacity can be increased. For example, when the outside air temperature is α-30 ° C. and the injection amount is increased by 30 to 40%, the heating capacity increases by about 8%.

Here, the opening degree of the third flow control device 123 is also examined. When the third flow control device 123 is opened to a certain degree of opening or more, the second flow control device 122 and the third flow control device 123 are connected in parallel. The flow rate decreases.
Considering the points described above, when the cooling / heating simultaneous operation is being performed and the outside air temperature is lower than a certain value during the heating main operation, the liquid pipe temperature detecting means 126 of the indoor unit D becomes a certain value or less. The cooling operation cannot be maintained. For this reason, priority is given to the injection amount to the compressor 101 at the same time as the liquid pipe temperature of the indoor unit D is raised by suppressing the opening of the third flow control device 123.
With this operation, a comfortable operation can be performed regardless of whether it is a cooling operation or a heating operation.
Considering such correlation characteristics, the opening degree of the second flow control device 122 and the opening degree of the third flow control device 123 will be described.

FIG. 6 illustrates an example of the correlation between the outside air temperature and the flow rate ratio according to the opening degree of the second flow control device 122 and the opening degree of the third flow control device 123 in Embodiment 1 of the present invention. FIG.
In FIG. 6, it is assumed that the reference temperature on the horizontal axis is α and the reference flow ratio on the vertical axis is β.
As shown in FIG. 6, when the outside air temperature is α-20 ° C., the flow rate of the third flow control device 123 is decreased and the flow rate of the second flow control device 122 is increased.
With this operation, the heating capacity can be increased. At this time, since the low pressure is also lowered, there is no influence on the cooling capacity.

Next, the correlation with the relay station B is also examined.
FIG. 7 shows the outside air temperature according to the opening of the second flow control device 122, the opening of the third flow control device 123, and the opening of the third flow regulator 115 in Embodiment 1 of the present invention. It is a figure explaining an example of the correlation with a flow rate ratio.
In FIG. 7, the third flow rate regulator 115 provided in the relay B that controls the differential pressure between the high pressure before and after the pressure detection means 127 a and 127 b and the intermediate pressure to be constant is the operation of the third flow control device 123. Similarly, as the outside air temperature decreases, the opening of the third flow rate regulator 115 is reduced.
With this operation, the pressure difference between the high pressure and the intermediate pressure is maintained constant, and at the same time, the liquid pipe temperature of the indoor unit D can be raised.
As a result, the cooling operation can be maintained.

FIG. 8 is a diagram illustrating an example of the correlation between the outside air temperature and the heating capacity ratio depending on whether or not there is proper control of the second flow control device 122 in Embodiment 1 of the present invention. .
As shown in FIG. 8, when the outside air temperature exceeds a certain value, the influence on the cooling capacity can be reduced by adjusting the appropriate opening degree of the second flow control device 122, and the stable cooling capacity. Can be maintained.

FIG. 9 is a diagram for explaining an example of the correlation between the outside air temperature and the heating capacity ratio depending on whether or not the fourth flow regulating valve 124 is appropriately controlled in Embodiment 1 of the present invention. .
As shown in FIG. 9, by adjusting the opening degree of the fourth flow rate adjustment valve 124, the influence on the cooling capacity can be reduced, and the stable cooling capacity can be maintained. For example, when the outside air temperature is low compared to a certain value, the opening degree of the fourth flow rate adjustment valve 124 is reduced, and when the outside air temperature is high compared to a certain value, the opening degree of the fourth flow rate adjustment valve 124. Increase
With this operation, the influence on the cooling capacity can be reduced, and a stable cooling capacity can be maintained.

As described above, by appropriately controlling the opening degree of the second flow rate control device 122, the third flow rate control device 123, and the third flow rate regulator 115 of the relay B according to the outside air temperature, Stable cooling operation can be continued while maintaining the heating capacity.
Therefore, highly efficient cooling and heating simultaneous operation can be performed.
In addition, in this Embodiment 1, although the cooling main operation and the heating main operation were demonstrated, it does not specifically limit to this. For example, only heating may be used.
Moreover, even if the number of heat source units A, the number of relay units B, and the number of indoor units are different from those in the first embodiment, the same effect can be obtained.
Moreover, even if an ice heat storage tank or a water heat storage tank (including hot water) is installed in series or in parallel with the heat source device side heat exchanger 103, the same effect is produced.
Furthermore, although the total of the connection pipes of the heat source machine A, the relay machine B, the first connection pipe 106, and the second connection pipe 107 is two, the total of the connection pipes is three. Can achieve the same effect.

Next, on the assumption of the above description, an operation example will be described with reference to the drawings.
FIG. 10 is a flowchart for explaining an operation example of the control unit 141 provided in the heat source machine A according to Embodiment 1 of the present invention.

(Step S11)
The controller 141 of the heat source device A determines whether or not the cooling and heating simultaneous operation is being performed. When the control unit 141 of the heat source device A determines that the cooling / heating simultaneous operation is being performed, the control unit 141 proceeds to step S12. On the other hand, when it determines with the control part 141 of the heat source machine A not being in simultaneous cooling and heating operation, it progresses to step S16.

(Step S12)
The control unit 141 of the heat source device A acquires the outside air temperature. For example, the outside temperature data detected by the outside temperature detecting means 131 is acquired.

(Step S13)
The control unit 141 of the heat source device A determines whether or not the outside air temperature corresponds to any of a plurality of predetermined threshold values.
For example, when the outside air temperature is equal to or lower than the injection start threshold (WB ° C.), the control unit 141 of the heat source device A proceeds to step S14. For example, as shown in FIG. 6, the injection start threshold (WB ° C.) corresponds to α-5 (WB ° C.), which is a start temperature at which the opening degree of the second flow control device 122 gradually increases. For α-5 (WB ° C.), for example, 0 ° C. is assumed.
In the above description, an example in which α-5 (WB ° C.) is 0 ° C. has been described, but the present invention is not particularly limited to this. The specific value of α-5 (WB ° C.) may be varied flexibly according to the surrounding environment and the operating condition of the air conditioner 1.

For example, when the outside air temperature is equal to or lower than the opening degree suppression threshold (WB ° C.), the control unit 141 of the heat source device A proceeds to step S15. The opening degree suppression threshold (WB ° C.) corresponds to α-20 (WB ° C.), which is a starting temperature at which the opening degree of the third flow control device 123 becomes small, as shown in FIG. 6, for example. As for α-20 (WB ° C.), for example, −15 ° C. is assumed.
Specifically, when either the indoor unit C or the indoor unit D is in the cooling operation and the outside air temperature reaches −15 ° C., the piping between the indoor unit being cooled and the second branching unit 111 The liquid pipe temperature of the tube drops, and the cooling operation cannot be continued. Therefore, when the outside air temperature is −15 ° C., the opening degree of the third flow control device 123 is narrowed to raise the liquid pipe temperature of the pipe and continue the cooling operation.
In the above description, an example in which α-20 (WB ° C.) is −15 ° C. has been described, but the present invention is not particularly limited to this. The specific value of α-20 (WB ° C.) may be varied in a flexible manner according to the surrounding environment and the operating status of the air conditioner 1.

Further, for example, the control unit 141 of the heat source device A proceeds to step S16 when the outside air temperature is other than that (injection start threshold value or opening degree suppression threshold value).

(Step S14)
The control part 141 of the heat source machine A increases the opening degree of the second flow rate control device 122 at a preset ratio. For example, as shown in FIG. 6, the ratio of the degree of opening that is gradually reduced is changed according to the outside air temperature.

(Step S15)
The control unit 141 of the heat source device A suppresses the opening degree of the third flow control device 123. For example, as shown in FIG. 6, when the outside air temperature is from α to α-20, the opening degree of the third flow control device 123 is fully open, but when the outside air temperature is α-20 or less, the third flow control device 123 is open. The opening degree of the flow control device 123 is narrowed down.

(Step S16)
The control unit 141 of the heat source machine A determines whether or not there is an end command. The control part 141 of the heat source machine A ends the process when there is an end command. On the other hand, if there is no termination command, the control unit 141 of the heat source machine A returns to step S12 and repeats the processing of steps S12 to S15.

FIG. 11 is a flowchart for explaining an operation example of the control unit 151 included in the relay station B according to Embodiment 1 of the present invention.

(Step S51)
The control unit 151 of the relay machine B sets the first ratio. As shown in FIG. 7, the first ratio is the ratio of the degree of opening for narrowing the third flow rate regulator 115 while the outside air temperature is higher than α-20 and lower than α.

(Step S52)
The control unit 151 of the relay B sets a second ratio that satisfies the condition that the second ratio> the first ratio. As shown in FIG. 7, the second ratio is the ratio of the degree of opening that narrows down the third flow regulator 115 when the outside air temperature is α−20 or less. As described above, when α-20 is assumed to be the outside air temperature at which the cooling operation cannot be continued, if the outside air temperature becomes α-20 or less, the cooling operation is not performed unless the liquid pipe temperature of the indoor unit during the cooling operation is increased. Can't continue. Therefore, the ratio to narrow down is set large.

(Step S53)
The control unit 151 of the relay machine B determines whether or not the cooling and heating simultaneous operation is being performed. When the air conditioner simultaneous operation is being performed, the control unit 151 of the relay machine B proceeds to step S54. On the other hand, the control part 151 of the relay machine B complete | finishes a process, when it is not in the air conditioning simultaneous operation.

(Step S54)
The control unit 151 of the relay machine B determines whether or not there is an end command. The control unit 151 of the relay machine B ends the process when there is an end command. On the other hand, if there is no termination command, the control unit 151 of the relay station B proceeds to step S55.

(Step S55)
The control unit 151 of the relay machine B acquires the high pressure side pressure value. For example, the control unit 151 of the relay machine B acquires the pressure value on the high pressure side among the pressure detection units 127a and 127b. Which is on the high voltage side may be determined by the control unit 151 of the relay B holding a correspondence table in which which corresponds to the high voltage side is registered in advance according to the operating state.

(Step S56)
The control unit 151 of the relay machine B acquires the intermediate pressure side pressure value. For example, the control unit 151 of the relay machine B acquires the pressure value on the intermediate pressure side among the pressure detection units 127a and 127b. Which is on the intermediate pressure side may be determined by the control unit 151 of the relay B holding a correspondence table in which which corresponds to the intermediate pressure side is registered in advance according to the operating state.

(Step S57)
The control unit 151 of the relay machine B obtains a differential pressure between the high pressure side pressure value and the intermediate pressure side pressure value.

(Step S58)
The control unit 151 of the relay B determines whether or not the differential pressure is constant. When the differential pressure is constant, the control unit 151 of the relay machine B proceeds to step S59. On the other hand, when the differential pressure is not constant, the control unit 151 of the relay station B proceeds to step S60.

(Step S59)
The control unit 151 of the relay machine B acquires the outside air temperature.

(Step S60)
The control unit 151 of the relay machine B makes the differential pressure constant by the third flow rate regulator 115.

(Step S61)
The control unit 151 of the relay machine B determines whether or not the outside air temperature corresponds to any of a plurality of predetermined threshold values.
For example, when the outside air temperature exceeds the second threshold value (WB ° C.) and is equal to or lower than the first threshold value (WB ° C.), the process proceeds to step S62.
For example, when the outside air temperature is equal to or lower than the second threshold (WB ° C.), the process proceeds to step S63.
For example, in other cases (when exceeding the first threshold (WB ° C.)), the process returns to step S54.

(Step S62)
The control unit 151 of the relay machine B suppresses the opening degree of the third flow rate regulator 115 at the first rate, and returns to step S54.

(Step S63)
The control unit 151 of the relay machine B suppresses the opening degree of the third flow rate regulator 115 at the second rate, and returns to step S54.

From the above description, the outside air temperature decreased during simultaneous cooling and heating operations by increasing the injection amount to one compressor and suppressing the refrigerant flow rate to the heat source side heat exchanger according to the outside air temperature. Even in this case, the cooling operation can be continued at a low cost while maintaining the heating capacity. Due to this configuration, highly efficient cooling and heating simultaneous operation can be performed.

As described above, in the first embodiment, one compressor 101 that compresses and discharges the refrigerant, the heat source machine side heat exchanger 103 that exchanges heat between the refrigerant and the surrounding heat source medium, the refrigerant and the surrounding utilization medium, Are provided between the plurality of usage side heat exchangers 105, the heat source unit side heat exchanger 103, and the usage side heat exchanger 105, and a part of the plurality of usage side heat exchangers 105 is cooled. And a relay unit B that switches a part of the plurality of use side heat exchangers 105 to the heating operation side, and among the plurality of use side heat exchangers 105, the cooling operation side and the heating are provided according to a control command. An air conditioner 1 that performs simultaneous cooling and heating operations by switching each of the plurality of use side heat exchangers 105 to any one of the operation side, between the relay unit B and the heat source unit side heat exchanger 103 The refrigerant that is provided and flows into the heat source machine side heat exchanger 103 An injection pipe 135 that is bypassed and supplied to one compressor 101; a second flow rate control device 122 that is provided in the injection pipe 135 and adjusts the flow rate of the refrigerant flowing into the one compressor 101; The third flow control device 123, which is connected in parallel to the flow control device 123 of the first flow control device and adjusts the flow rate of the refrigerant flowing into the heat source apparatus side heat exchanger 103, the second flow control device 122, and the third flow control device. The control unit 141 adjusts the opening degree of the second flow rate control device 122 and the opening degree of the third flow rate control device 123 according to the outside air temperature. Even when the outside air temperature decreases during the simultaneous operation, the cooling operation can be continued while maintaining the heating capacity at low cost. Due to this configuration, highly efficient cooling and heating simultaneous operation can be performed.

A heat source machine, B relay machine, C, D indoor unit, 1 air conditioner, 101 compressor, 102 four-way valve, 103 heat source machine side heat exchanger, 104 accumulator, 105, 105c, 105d use side heat exchanger, 106 106c, 106d, first connecting pipe, 107, 107c, 107d, second connecting pipe, 108, 108a, 108b, solenoid valve, 109, 109c, 109d, first flow regulator, 110, first branch, 111, first 2 branches, 112 gas-liquid separator, 113 second flow rate regulator, 114 bypass piping, 115 third flow rate regulator, 116 first heat exchanger, 117 second heat exchanger, 118-121 137a, 137b check valve, 122 second flow control device, 123 third flow control device, 124 fourth flow control valve 125 temperature detector, 126,126C, 126d liquid pipe temperature detection means, 127,127A, 127b pressure detecting means, 131 outdoor air temperature detecting means, 135 injection line, 137a_all, 137b_all association portion, 141 and 151 control unit.

Claims

One compressor that compresses and discharges the refrigerant;
A heat source side heat exchanger that exchanges heat between the refrigerant and the surrounding heat source medium;
A plurality of use side heat exchangers for exchanging heat between the refrigerant and the surrounding use medium;
Provided between the heat source unit side heat exchanger and the use side heat exchanger, a part of the plurality of use side heat exchangers is switched to a cooling operation side, and one of the plurality of use side heat exchangers A relay unit for switching the part to the heating operation side,
According to a control command, among the plurality of use side heat exchangers, the cooling and heating simultaneous operation is performed by switching each of the plurality of use side heat exchangers to either the cooling operation side or the heating operation side. An air conditioner,
An injection pipe that is provided between the relay machine and the heat source machine side heat exchanger, bypasses the refrigerant flowing into the heat source machine side heat exchanger, and supplies the refrigerant to the one compressor;
A compressor flow controller for adjusting a flow rate of the refrigerant that is provided in the injection pipe and flows into the one compressor;
A flow control device for heat source side heat exchanger that is connected in parallel with the flow rate control device for compressor and adjusts the flow rate of the refrigerant flowing into the heat source side heat exchanger;
A controller for adjusting the flow rate control device for the compressor and the flow rate control device for the heat source unit side heat exchanger, and
The controller is
An air conditioner that adjusts an opening degree of the compressor flow rate control device and an opening degree of the heat source unit side heat exchanger flow control device according to an outside air temperature.
The controller is
An injection start threshold for starting the supply of the refrigerant from the injection pipe is set,
An opening degree suppression threshold for reducing the flow rate of the refrigerant passing through the heat source unit side heat exchanger flow control device is set,
If the outside air temperature is less than or equal to the injection start threshold, increase the opening of the compressor flow control device at a preset rate,
2. The air conditioner according to claim 1, wherein when the outside air temperature is equal to or less than the opening degree suppression threshold, the opening degree of the heat source unit side heat exchanger flow control device is reduced.
The repeater is
A flow rate regulator that is connected in series with the flow rate control device for the compressor and the flow rate control device for the heat source side heat exchanger, and that adjusts the flow rate of the refrigerant flowing through the relay,
The air conditioner according to claim 2, wherein an opening degree of the flow rate regulator is adjusted in accordance with the outside air temperature.
The repeater is
A first ratio and a first threshold value corresponding to the first ratio are set;
A second ratio that is larger than the first ratio and a second threshold value corresponding to the second ratio are set;
When the outside air temperature is less than or equal to the first threshold, the opening of the flow rate regulator is reduced by the first rate,
4. The air conditioner according to claim 3, wherein when the outside air temperature is equal to or lower than the second threshold, the opening degree of the flow rate regulator is decreased by the second ratio.
Provided between the relay machine and the heat source machine side heat exchanger, connected in parallel with the heat source machine side heat exchanger flow control device, comprising a flow rate adjustment valve for adjusting the flow rate of the refrigerant,
The controller is
The air conditioner according to claim 4, wherein an opening degree of the flow rate adjusting valve is adjusted according to the outside air temperature.
The controller is
When the outside air temperature is equal to or lower than the injection start threshold, by adjusting the opening of the compressor flow control device, among the amount of refrigerant supplied from the relay, the amount of refrigerant flowing to the compressor is increased,
When the outside air temperature is equal to or less than the opening degree suppression threshold, among the amount of refrigerant supplied from the relay machine by adjusting the opening degree of the heat source unit side heat exchanger flow control device and the opening degree of the flow rate adjustment valve, The air conditioner according to claim 5, wherein the amount of refrigerant flowing to the heat source unit side heat exchanger is reduced.