[go: up one dir, main page]

WO2014054090A1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

Info

Publication number
WO2014054090A1
WO2014054090A1 PCT/JP2012/075309 JP2012075309W WO2014054090A1 WO 2014054090 A1 WO2014054090 A1 WO 2014054090A1 JP 2012075309 W JP2012075309 W JP 2012075309W WO 2014054090 A1 WO2014054090 A1 WO 2014054090A1
Authority
WO
WIPO (PCT)
Prior art keywords
flow rate
control device
heat exchanger
refrigerant
heat source
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2012/075309
Other languages
English (en)
Japanese (ja)
Inventor
博文 ▲高▼下
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to EP12886159.8A priority Critical patent/EP2905560A4/fr
Priority to US14/420,761 priority patent/US20150219373A1/en
Priority to PCT/JP2012/075309 priority patent/WO2014054090A1/fr
Priority to JP2014539487A priority patent/JPWO2014054090A1/ja
Publication of WO2014054090A1 publication Critical patent/WO2014054090A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves

Definitions

  • 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).
  • 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).
  • the conventional air conditioner (Patent Document 1)
  • a plurality of compressors 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.
  • 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.
  • 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
  • FIG. 1 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
  • FIG. 1 is a diagram illustrating a configuration example of an air-conditioning apparatus 1 according to Embodiment 1 of the present invention.
  • 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.
  • 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.
  • 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.
  • the relay machine B and the indoor unit C are connected by the 1st connection piping 106c and the 2nd connection piping 107c.
  • the relay machine B and the indoor unit D are connected by the 1st connection piping 106d and the 2nd connection piping 107d.
  • the relay unit B relays the refrigerant flowing between the heat source unit A, the indoor unit C, and the indoor unit D.
  • the present invention is not particularly limited thereto.
  • the case where two or more indoor units are provided may be used.
  • a plurality of heat source machines may be used.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the example in which the outside temperature detecting means 131 is a thermistor has been described.
  • 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.
  • 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.
  • 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.
  • 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.
  • the relay unit B includes the third flow rate regulator 115 and adjusts the amount of refrigerant to the heat source unit A side.
  • 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.
  • 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.
  • 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.
  • the indoor unit C side is opened, and the indoor unit D side is closed.
  • 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 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.
  • 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.
  • 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.
  • the use side heat exchanger 105d exchanges heat with a use medium such as air, and condenses and liquefies the supplied gaseous refrigerant.
  • 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.
  • the first connection pipe 106 has a low pressure
  • 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.
  • 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.
  • the supplied liquid refrigerant passes through the check valve 108d connected to the indoor unit C and flows into the indoor unit C.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the indoor unit C side is closed and the indoor unit D side is opened.
  • 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 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the first connection pipe 106 has a low pressure
  • 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.
  • 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.
  • the reference temperature on the horizontal axis is ⁇ and the reference heating capacity ratio on the vertical axis is ⁇ .
  • 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.
  • the high-pressure pressure increases and the heating capacity can be increased.
  • the heating capacity increases by about 8%.
  • the opening degree of the third flow control device 123 is also examined.
  • 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.
  • the liquid pipe temperature detecting means 126 of the indoor unit D becomes a certain value or less.
  • the cooling operation cannot be maintained.
  • 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.
  • 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. 6 it is assumed that the reference temperature on the horizontal axis is ⁇ and the reference flow ratio on the vertical axis is ⁇ .
  • 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.
  • 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.
  • 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.
  • 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. .
  • the opening degree of the fourth flow rate adjustment valve 124 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the injection start threshold (WB ° C.) corresponds to ⁇ -5 (WB ° C.), which is a start temperature at which the opening degree of the second flow control device 122 gradually increases.
  • ⁇ -5 (WB ° C.) for example, 0 ° C. is assumed. In the above description, an example in which ⁇ -5 (WB ° C.) is 0 ° C. has been described, but the present invention is not particularly limited to this.
  • the specific value of ⁇ -5 (WB ° C.) may be varied flexibly according to the surrounding environment and the operating condition of the air conditioner 1.
  • the control unit 141 of the heat source device A proceeds to step S15.
  • the opening degree suppression threshold (WB ° C.) corresponds to ⁇ -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.
  • ⁇ -20 (WB ° C.) for example, ⁇ 15 ° C. is assumed.
  • 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 ⁇ to ⁇ -20, the opening degree of the third flow control device 123 is fully open, but when the outside air temperature is ⁇ -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.
  • 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 ⁇ -20 and lower than ⁇ .
  • 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.
  • 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 ⁇ 20 or less.
  • ⁇ -20 is assumed to be the outside air temperature at which the cooling operation cannot be continued, if the outside air temperature becomes ⁇ -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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
PCT/JP2012/075309 2012-10-01 2012-10-01 Dispositif de climatisation Ceased WO2014054090A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP12886159.8A EP2905560A4 (fr) 2012-10-01 2012-10-01 Dispositif de climatisation
US14/420,761 US20150219373A1 (en) 2012-10-01 2012-10-01 Air-conditioning apparatus
PCT/JP2012/075309 WO2014054090A1 (fr) 2012-10-01 2012-10-01 Dispositif de climatisation
JP2014539487A JPWO2014054090A1 (ja) 2012-10-01 2012-10-01 空気調和装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/075309 WO2014054090A1 (fr) 2012-10-01 2012-10-01 Dispositif de climatisation

Publications (1)

Publication Number Publication Date
WO2014054090A1 true WO2014054090A1 (fr) 2014-04-10

Family

ID=50434452

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/075309 Ceased WO2014054090A1 (fr) 2012-10-01 2012-10-01 Dispositif de climatisation

Country Status (4)

Country Link
US (1) US20150219373A1 (fr)
EP (1) EP2905560A4 (fr)
JP (1) JPWO2014054090A1 (fr)
WO (1) WO2014054090A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103759455B (zh) * 2014-01-27 2015-08-19 青岛海信日立空调系统有限公司 热回收变频多联式热泵系统及其控制方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009186121A (ja) * 2008-02-07 2009-08-20 Mitsubishi Electric Corp ヒートポンプ式給湯用室外機及びヒートポンプ式給湯装置
JP2010139215A (ja) * 2008-12-15 2010-06-24 Mitsubishi Electric Corp 空気調和装置
WO2010128557A1 (fr) * 2009-05-08 2010-11-11 三菱電機株式会社 Climatiseur
JP4675810B2 (ja) 2006-03-28 2011-04-27 三菱電機株式会社 空気調和装置
WO2012104893A1 (fr) * 2011-01-31 2012-08-09 三菱電機株式会社 Dispositif de climatisation

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2723953B2 (ja) * 1989-02-27 1998-03-09 株式会社日立製作所 空気調和装置
US6510698B2 (en) * 1999-05-20 2003-01-28 Mitsubishi Denki Kabushiki Kaisha Refrigeration system, and method of updating and operating the same
JP4356214B2 (ja) * 2000-08-21 2009-11-04 三菱電機株式会社 油分離器および室外機
KR100471453B1 (ko) * 2002-11-22 2005-03-08 엘지전자 주식회사 히트펌프 시스템 및 히트펌프 시스템의 전자 팽창밸브제어방법
WO2007110908A1 (fr) * 2006-03-27 2007-10-04 Mitsubishi Denki Kabushiki Kaisha Dispositif de climatisation frigorifique
WO2009098751A1 (fr) * 2008-02-04 2009-08-13 Mitsubishi Electric Corporation Système complexe de climatisation et de chauffe-eau
WO2010050003A1 (fr) * 2008-10-29 2010-05-06 三菱電機株式会社 Climatiseur
EP2341297B1 (fr) * 2008-10-29 2019-09-25 Mitsubishi Electric Corporation Conditionneur d'air
CN102112817B (zh) * 2008-10-29 2014-04-30 三菱电机株式会社 空调装置
EP2309199B1 (fr) * 2008-10-29 2021-08-18 Mitsubishi Electric Corporation Climatiseur
EP2312229B1 (fr) * 2008-10-29 2018-11-21 Mitsubishi Electric Corporation Climatiseur
JP5236008B2 (ja) * 2008-10-29 2013-07-17 三菱電機株式会社 空気調和装置
EP2341295B1 (fr) * 2008-10-29 2018-05-30 Mitsubishi Electric Corporation Climatiseur
US8974274B2 (en) * 2010-04-16 2015-03-10 Google Inc. Evaporative induction cooling
JP5663208B2 (ja) * 2010-06-21 2015-02-04 株式会社赤ん坊カンパニー 折畳式ハンガーホルダー及びハンガーセット
CN103154622B (zh) * 2010-10-12 2016-02-10 三菱电机株式会社 热介质转换机以及搭载该热介质转换机的空调装置
JP5730335B2 (ja) * 2011-01-31 2015-06-10 三菱電機株式会社 空気調和装置
CN104053959B (zh) * 2012-01-23 2016-03-30 三菱电机株式会社 空气调节装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4675810B2 (ja) 2006-03-28 2011-04-27 三菱電機株式会社 空気調和装置
JP2009186121A (ja) * 2008-02-07 2009-08-20 Mitsubishi Electric Corp ヒートポンプ式給湯用室外機及びヒートポンプ式給湯装置
JP2010139215A (ja) * 2008-12-15 2010-06-24 Mitsubishi Electric Corp 空気調和装置
WO2010128557A1 (fr) * 2009-05-08 2010-11-11 三菱電機株式会社 Climatiseur
WO2012104893A1 (fr) * 2011-01-31 2012-08-09 三菱電機株式会社 Dispositif de climatisation

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2905560A4

Also Published As

Publication number Publication date
EP2905560A4 (fr) 2016-05-18
JPWO2014054090A1 (ja) 2016-08-25
EP2905560A1 (fr) 2015-08-12
US20150219373A1 (en) 2015-08-06

Similar Documents

Publication Publication Date Title
US10161647B2 (en) Air-conditioning apparatus
US10222081B2 (en) Air-conditioning apparatus
KR102344058B1 (ko) 공기조화 시스템 및 그 제어방법
JP6223469B2 (ja) 空気調和装置
CN101065623B (zh) 空调装置
KR20070065417A (ko) 냉동 공조장치, 냉동 공조장치의 운전 제어 방법, 냉동공조장치의 냉매량 제어 방법
US10139125B2 (en) Air-conditioning apparatus
US10415846B2 (en) Air-conditioning apparatus
JPWO2016157519A1 (ja) 空気調和装置
WO2015198475A1 (fr) Dispositif à cycle frigorifique
WO2014091909A1 (fr) Dispositif de chauffage du type pompe à chaleur
WO2017138108A1 (fr) Dispositif de climatisation
JP5759080B2 (ja) 空気調和装置
EP2515055B1 (fr) Climatiseur
US9903625B2 (en) Air-conditioning apparatus
JP6198945B2 (ja) 空気調和装置
KR20140125141A (ko) 공기조화 시스템
WO2014054154A1 (fr) Dispositif de conditionnement d'air
WO2014054090A1 (fr) Dispositif de climatisation
KR20150074639A (ko) 공기조화 시스템 및 그 제어방법
KR20140125242A (ko) 공기조화 시스템
JPH04283363A (ja) 冷凍装置
JPH04283358A (ja) 冷凍装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12886159

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2014539487

Country of ref document: JP

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 14420761

Country of ref document: US

REEP Request for entry into the european phase

Ref document number: 2012886159

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2012886159

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE