WO2015177896A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2015177896A1 WO2015177896A1 PCT/JP2014/063520 JP2014063520W WO2015177896A1 WO 2015177896 A1 WO2015177896 A1 WO 2015177896A1 JP 2014063520 W JP2014063520 W JP 2014063520W WO 2015177896 A1 WO2015177896 A1 WO 2015177896A1
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- WIPO (PCT)
- Prior art keywords
- valve
- refrigerant
- heat exchanger
- indoor unit
- flow rate
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/32—Responding to malfunctions or emergencies
- F24F11/36—Responding to malfunctions or emergencies to leakage of heat-exchange fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
Definitions
- the present invention relates to an air conditioner that supplies hot and cold produced by a heat source machine, or both hot and cold to a plurality of load-side units, and particularly to a refrigerant circuit thereof.
- an indoor unit A load side unit (indoor unit) having a side heat exchanger is connected by a refrigerant pipe to constitute a refrigerant circuit for circulating the refrigerant. Then, in the indoor unit side heat exchanger, when the refrigerant evaporates and condenses, the heat, heat is released from the air in the air-conditioning target space to be heat exchanged, and the pressure, temperature, etc. related to the refrigerant in the refrigerant circuit are changed. Air conditioning is performed while changing.
- the refrigerant used in such an air conditioner for example, an HFC (hydrofluorocarbon) refrigerant is often used.
- CO 2 natural refrigerant
- the multiple indoor units automatically determine the cooling and heating respectively, and the indoor unit is cooled and heated.
- an air-conditioning apparatus capable of simultaneous cooling and heating operation (cooling and heating mixed operation) that can be performed (see, for example, Patent Document 1).
- the valve device of the first branching section in the relay has two valves connected in parallel, one being the first connection pipe and the other being the first connection pipe. It is connected to the second connection pipe.
- the temperature of the refrigerant flowing into the indoor unit that is in the heating operation because heat is transferred from the high-temperature refrigerant gas to the cold refrigerant gas by integrating or integrating the valves. Decreases. For this reason, there is a problem that indoor comfort and energy saving are deteriorated.
- the switching valve is closed when the refrigerant leaks, but the refrigerant pressure in the pipe rises and the refrigerant leaks to the indoor unit side. was there.
- the present invention has been made to solve the above-described problems, and a first object is to move to the indoor unit side even when there is a crack in the piping or the loosening of the pipe connection portion on the indoor unit side. It is in obtaining the air conditioning apparatus which can suppress the refrigerant
- the second object is to obtain an air conditioner that can suppress the generation of refrigerant flow noise by adjusting the flow rate of a valve connected to the first connection pipe when switching from heating operation to cooling operation. It is in.
- the third purpose is that even if there are multiple use side heat exchangers that are performing cooling or heating operations during simultaneous cooling and heating operations, it is possible to manufacture with inexpensive materials without reducing performance This is to obtain an air conditioner.
- An air conditioner includes a compressor that compresses and discharges a refrigerant, a first switching valve that switches a flow path of the refrigerant discharged from the compressor, a refrigerant that has passed through the first switching valve, and a surrounding area.
- a heat source machine side heat exchanger that exchanges heat with the heat source medium
- a use side heat exchanger that exchanges heat between the refrigerant that has passed through the first switching valve and the surrounding use medium.
- a plurality of indoor units each mounted with a flow controller connected to the use side heat exchanger, and provided between the heat source unit and the indoor unit, the first connection between the heat source unit and each indoor unit Connect via the pipe and the second connection pipe, switch part of the use side heat exchanger of the plurality of indoor units to the cooling operation side, and switch the other part of the use side heat exchanger to the heating operation side
- An air conditioner having a function, wherein the repeater is configured to use a heat exchanger on a use side on a cooling operation side.
- a second branch part that connects the third switch valve to the second connection pipe, and the third switch valve provided in the second branch part has a predetermined pressure or higher. And has a function of releasing pressure.
- the switching valve provided in the first and second branch portions is closed to eliminate the movement of the refrigerant to the indoor unit side. Since the switching valve of the branch portion has a function of detecting a pressure equal to or higher than a predetermined pressure and releasing the pressure, the pressure of the refrigerant in the indoor unit can be reduced to suppress the refrigerant from flowing into the room to the minimum.
- FIG. 1 shows the structural example of the air conditioning apparatus in Embodiment 1 of this invention. It is a figure which shows the structural example of the air conditioning apparatus which concerns on the driving
- FIG. 1 is a diagram illustrating a configuration example of an air conditioner.
- the air conditioner of the first embodiment will be described by taking, for example, a building multi-air conditioner as an example.
- 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 relay machine B and the heat source machine A are connected by a first connection pipe 106 and a second connection pipe 107.
- the second connection pipe 107 has a smaller pipe diameter than the first connection pipe 106.
- the indoor unit C and the relay unit B are connected by a first connection pipe 106c and a second connection pipe 107c. Moreover, the indoor unit D and the relay machine B 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.
- 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 compressor 101 is provided between the four-way valve 102 and the accumulator 104.
- the compressor 101 sucks the refrigerant and compresses and discharges the refrigerant.
- the suction side of the compressor 101 is connected to the accumulator 104, and the discharge side is connected to the four-way valve 102.
- the four-way valve 102 has four ports.
- the first port is the discharge side of the compressor 101
- the second port is the heat source machine side heat exchanger 103
- the third port is the accumulator 104
- the fourth port is the check valve 119.
- the four-way valve 102 is connected to the outlet side and the inlet side of the check valve 120, and switches the refrigerant flow path.
- the four-way valve 102 corresponds to the “first switching valve” in the present invention.
- the heat source machine side heat exchanger 103 is provided between the four-way valve 102, the check valve 118, and the check valve 121.
- One of the heat source apparatus side heat exchangers 103 is connected to a pipe connected to the four-way valve 102 and the other connected to the inlet side of the check valve 118 and the outlet side of the check valve 121.
- the heat source device side heat exchanger 103 performs heat exchange between the refrigerant flowing in the heat source device side heat exchanger 103 and the medium flowing outside the heat source device side heat exchanger 103.
- the medium flowing outside the heat source apparatus side heat exchanger 103 includes water and brine.
- the accumulator 104 is connected between the four-way valve 102 and the suction side of the compressor 101.
- the accumulator 104 separates the liquid refrigerant and supplies the gas refrigerant to the compressor 101.
- the compressor 101, the four-way valve 102, the heat source device side heat exchanger 103, and the accumulator 104 described above constitute a part of the refrigerant circuit.
- the check valve 118 is provided between the outlet side of the heat source apparatus side heat exchanger 103 and the check valve 121 and the outlet side of the second connection pipe 107 and the check valve 120.
- the inlet side of the check valve 118 is connected to piping connected to the heat source apparatus side heat exchanger 103 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 from the heat source unit side heat exchanger 103 to the second connection pipe 107 only from one direction.
- 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 connecting 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 inlet side of the four-way valve 102 and 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 and the outlet side of the second connection pipe 107 and the check valve 118.
- the inlet side of the check valve 120 is connected to a pipe connected to the outlet side of the four-way valve 102 and the check valve 119.
- the outlet side of the check valve 120 is connected to the second connection pipe 107 and a pipe connected to the outlet side of the check valve 118.
- 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 is provided between the inlet side of the first connection pipe 106 and the check valve 119 and the inlet side of the heat source apparatus side heat exchanger 103 and the check valve 118.
- the inlet side of the check valve 121 is connected to the first connection pipe 106 and a pipe connected to the inlet side of the check valve 119.
- the outlet side of the check valve 121 is connected to a pipe connected to the inlet side of the heat source apparatus side heat exchanger 103 and the check valve 118.
- 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.
- the check valve 118 to the check valve 121 described above constitute a refrigerant circuit flow path switching valve.
- a refrigerant circuit flow path switching valve and a relay unit B, an indoor unit C, and an indoor unit D, which will be described in detail later, during the cooling and heating simultaneous operation, a cooling cycle in the refrigerant circuit, a cooling cycle in the heating operation, Is formed.
- 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, first pressure detection means 122, second pressure detection means 123, temperature detection means 125, 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 section 110 is connected to the indoor unit C through the first connection pipe 106c, and is connected to the indoor unit D through the first connection pipe 106d.
- the 1st branch part 110 is provided with the flow regulating valve 108a and the electromagnetic valve 108b.
- the flow rate adjusting valve 108a and the electromagnetic valve 108b are separated in the first branch part 110.
- the flow control valve 108a and the electromagnetic valve 108b on the indoor unit C side are connected to the indoor unit C via the first connection pipe 106c.
- the flow control valve 108a on the indoor unit C side has one end connected to the first connection pipe 106 and the other end connected to one terminal of the first connection pipe 106c and the electromagnetic valve 108b.
- the other terminal of the electromagnetic valve 108 b is connected to the second connection pipe 107.
- the flow rate adjustment valve 108a on the indoor unit C side can be opened and closed and the flow rate can be adjusted.
- the flow control valve 108a and the electromagnetic valve 108b on the indoor unit D side are connected to the indoor unit D through the first connection pipe 106d.
- the flow control valve 108a on the indoor unit D side has one end connected to the first connection pipe 106 and the other end connected to one terminal of the first connection pipe 106d and the electromagnetic valve 108b.
- the other terminal of the electromagnetic valve 108 b is connected to the second connection pipe 107.
- the flow rate adjustment valve 108a on the indoor unit D side can be opened and closed and the flow rate can be adjusted.
- 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 branch 110 connects the first connection pipe 106c to the first connection pipe 106 or the second connection pipe 107 using the flow rate adjustment valve 108a and the electromagnetic valve 108b.
- the 1st branch part 110 connects the 1st connection piping 106d to the 1st connection piping 106 or the 2nd connection piping 107 using the flow regulating valve 108a and the electromagnetic valve 108b.
- the flow rate adjusting valve 108a and the electromagnetic valve 108b correspond to the “second switching valve” in the present invention.
- the second branching unit 111 includes a pressure relief valve 124a that operates when a pressure equal to or higher than a predetermined pressure is detected (for example, set to a design pressure or less so as not to exceed the design pressure), and a solenoid valve 124b.
- the pressure relief valve 124a and the electromagnetic valve 124b are connected to each other in an antiparallel relationship.
- the pressure relief valve 124a and the solenoid valve 124b correspond to the “third switching valve” in the present invention.
- the pressure relief valve 124a corresponds to the “function of detecting a pressure higher than a predetermined pressure and releasing the pressure” in the present invention.
- the second branch portion 111 is connected to the indoor unit C via the second connection pipe 107c.
- the input side of the pressure relief valve 124a on the indoor unit C side and the output side of the electromagnetic valve 124b are connected to the indoor unit C via the second connection pipe 107c.
- the second branch portion 111 is connected to the indoor unit D through the second connection pipe 107d.
- the input side of the pressure relief valve 124a on the indoor unit D side and the output side of the electromagnetic valve 124b are connected to the indoor unit D via the second connection pipe 107d.
- the output side of the pressure relief valve 124a is connected to the meeting part 124a_all.
- the input side of the electromagnetic valve 124b is connected to the meeting part 124b_all.
- the second branch portion 111 is connected to the second flow rate regulator 113 and the second heat exchanger 117 via the meeting portion 124a_all.
- the second branch part 111 is connected to the third flow rate regulator 115 and the second heat exchanger 117 via the meeting part 124b_all.
- the gas-liquid separator 112 is provided in the middle of the second connection pipe 107.
- the gas phase part of the gas-liquid separator 112 is connected to the electromagnetic valve 108 b of the first branch part 110.
- the liquid phase part of the gas-liquid separator 112 passes through the first heat exchanger 116, the second flow rate regulator 113, the second heat exchanger 117, and the third flow rate regulator 115. 2 branching portions 111 are connected.
- 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 124a_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 first pressure detection means 122 to be described later in detail.
- the pipe connected between the second flow rate regulator 113, the second heat exchanger 117, and the meeting part 124a_all is provided with a second pressure detecting means 123, which will be described later in detail.
- the second flow rate regulator 113 is a flow rate regulator whose opening degree can be adjusted, and the difference between the pressure value detected by the first pressure detection means 122 and the pressure value detected by the second pressure detection means 123. Adjust the opening so that becomes constant.
- the third flow rate regulator 115 has one end connected to the bypass pipe 114 side of the second heat exchanger 117 and the other end connected to the pipe side connecting the meeting portion 124b_all and the second heat exchanger 117. .
- the third flow rate regulator 115 is a flow rate regulator whose opening degree can be adjusted, and any one of the temperature detection means 125, the first pressure detection means 122, the second pressure detection means 123, or a combination thereof. Adjust the opening.
- 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. For this reason, according to the opening degree of the 3rd flow regulator 115, the quantity of the refrigerant
- 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.
- the first heat exchanger 116 performs heat exchange between a pipe provided between the gas-liquid separator 112 and the second flow rate regulator 113 and the bypass pipe 114.
- 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 124b_all.
- the second heat exchanger 117 performs heat exchange between a pipe provided between the second flow rate regulator 113 and the third flow rate regulator 115 and the bypass pipe 114.
- the temperature detection means 125 is formed by a thermistor, for example.
- the temperature detection means 125 measures the temperature of the refrigerant flowing through the outlet of the second heat exchanger 117, that is, the pipe provided on the downstream side of the second heat exchanger 117, and sends 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 detecting means 125 has been described as being formed of a thermistor, but the present invention is not limited to this.
- the first pressure detection means 122 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 sends the measurement result to the control unit 151.
- the second pressure detecting means 123 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, The measurement result is supplied to the control unit 151.
- the control unit 151 is configured mainly with a microprocessor unit, for example, and performs overall control of the entire relay unit B, communication with an external device such as the heat source unit A, various calculations, and the like.
- the indoor unit C includes a use side heat exchanger 105c, a first flow rate regulator 109c, and the like.
- One end of the use side heat exchanger 105c is connected to the first connection pipe 106c, and the other end is connected to the first flow rate regulator 109c.
- One end of the first flow regulator 109c is connected to the use side heat exchanger 105c, and the other end is connected to the second connection pipe 107c.
- a plurality of usage-side heat exchangers 105c are provided, and the usage-side heat exchanger 105c and the first flow rate regulator 109c constitute a part of the refrigerant circuit.
- the indoor unit D includes a use-side heat exchanger 105d, a first flow rate regulator 109d, and the like.
- One end of the use side heat exchanger 105d is connected to the first connection pipe 106d, and the other end is connected to the first flow rate regulator 109d.
- one end of the first flow rate regulator 109d is connected to the use side heat exchanger 105d, and the other end is connected to the second connection pipe 107d.
- a plurality of usage-side heat exchangers 105d are provided, and the usage-side heat exchanger 105d and the first flow rate regulator 109d constitute a part of the refrigerant circuit.
- the present invention is not limited to this.
- the number of indoor units may be three or more, or the number of heat source units A may be two or more.
- the case where there are two or more repeaters B may be used.
- FIG. 2 is a diagram illustrating a configuration example of the air conditioner 1 according to the cooling-main operation state during the simultaneous cooling and heating operation in the first embodiment.
- the cooling operation is set for the indoor unit C and the heating operation is set for the indoor unit D, and the operation of the air conditioner 1 is performed mainly by the cooling.
- the flow control valve 108a and the electromagnetic valve 124b on the indoor unit C side are opened, and the electromagnetic valve 108b is closed.
- the flow rate adjustment valve 108a and the electromagnetic valve 124b on the indoor unit D side are closed, and the electromagnetic valve 108b is opened.
- the opening degree of the second flow rate regulator 113 is controlled so that the differential pressure between the first pressure detection means 122 and the second pressure detection means 123 becomes an appropriate value.
- the refrigerant is compressed by the compressor 101, and the discharged high-temperature and high-pressure gas refrigerant flows into the heat source apparatus side heat exchanger 103 through the four-way valve 102.
- the refrigerant passing through the heat source apparatus side heat exchanger 103 is heat exchanged with a heat source medium such as 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 through the check valve 118 and is supplied to the gas-liquid separator 112 of the relay B.
- the gas-liquid two-phase high-temperature and high-pressure refrigerant is separated into a gaseous refrigerant and a liquid refrigerant by the gas-liquid separator 112.
- the separated gaseous refrigerant flows into the first branch portion 110 as indicated by the thick dotted arrow.
- the gaseous refrigerant that has flowed into the first branch section 110 is supplied to the indoor unit D in which the heating operation is set, through the electromagnetic valve 108b and the first connection pipe 106d that are open on the indoor unit D side. .
- the use side heat exchanger 105d exchanges heat with a use medium such as air, and condenses and liquefies the supplied gaseous refrigerant.
- the use side heat exchanger 105d is controlled by the first flow rate regulator 109d based on the degree of supercooling at the outlet of the use 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 to an intermediate pressure refrigerant that is an intermediate pressure between the high pressure and the low pressure.
- the refrigerant having reached the intermediate pressure passes through the pressure relief valve 124 a and flows into the second branch portion 111.
- the liquid refrigerant separated by the gas-liquid separator 112 passes through the second flow rate regulator 113 that controls the differential pressure 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 electromagnetic valve 124b connected to the indoor unit C and flows into the indoor unit C.
- the inflowing liquid refrigerant is depressurized to a low pressure by the first flow rate regulator 109c controlled according to the degree of superheat at the outlet of the use side heat exchanger 105c of the indoor unit C, and then used on 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.
- the flow regulating valve 108a connected with the indoor unit C is opening. Therefore, the inflowing gas refrigerant passes through the flow rate adjustment valve 108 a 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. Thereafter, the gas refrigerant is sucked into the compressor 101 through the four-way valve 102 and the accumulator 104.
- the first connection pipe 106 is at a low pressure
- the second connection pipe 107 is at a high pressure. Therefore, the refrigerant flows through the check valve 118 and the check valve 119 due to the pressure difference between the two pipes, but the refrigerant does not flow through the check valve 120 and the check valve 121.
- 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 been lowered exchanges heat with the liquid refrigerant mainly supplied from the second flow rate regulator 113 in the second heat exchanger 117 while passing through the bypass pipe 114. Thus, it becomes a gas-liquid two-phase refrigerant.
- heat exchange is performed with the high-temperature and high-pressure liquid refrigerant supplied from the gas-liquid separator 112, thereby becoming a gas refrigerant and flowing into the first connection pipe 106. .
- the gas refrigerant is sucked into the compressor 101 through the four-way valve 102 and the accumulator 104.
- FIG. 3 is a diagram illustrating a configuration example of the air-conditioning apparatus 1 according to the heating-main operation state during the simultaneous cooling and heating operation in the first embodiment.
- heating operation is set for the indoor unit C and cooling operation is set for the indoor unit D, and the operation of the air conditioner 1 is performed mainly by heating.
- the flow control valve 108a and the electromagnetic valve 124b on the indoor unit C side are closed, and the electromagnetic valve 108b is opened.
- the flow control valve 108a and the electromagnetic valve 124b on the indoor unit D side are opened, and the electromagnetic valve 108b is closed.
- the opening degree of the second flow rate regulator 113 is controlled so that the differential pressure between the first pressure detection means 122 and the second pressure detection means 123 becomes an appropriate value.
- the refrigerant is compressed by the compressor 101 and discharged.
- the discharged high-temperature and high-pressure gas refrigerant passes through the second connection pipe 107 through the four-way valve 102 and the check valve 120 and is supplied to the gas-liquid separator 112 of the relay unit B.
- 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 section 110 is supplied to the indoor unit C in which the heating operation is set, through the electromagnetic valve 108b and the first connection pipe 106c that are open on the indoor unit C side. .
- 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 refrigerant passing through 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 to an intermediate pressure liquid refrigerant that is an intermediate pressure between the high pressure and the low pressure.
- the liquid refrigerant having the intermediate pressure passes through the pressure relief valve 124 a and flows into the second branch portion 111.
- the liquid refrigerant that has flowed into the second branch part 111 joins at the meeting part 124a_all.
- the liquid refrigerant merged at the meeting part 124a_all passes through the second heat exchanger 117.
- part of the liquid refrigerant that has passed through the second heat exchanger 117 passes through the third flow rate regulator 115.
- the liquid refrigerant that has passed through the third flow regulator 115 is decompressed by the third flow regulator 115 and flows into the second heat exchanger 117.
- the low-pressure liquid refrigerant exchanges heat with the intermediate-pressure liquid refrigerant, and the low-pressure liquid refrigerant becomes a gas refrigerant because the evaporation temperature is low.
- the gas refrigerant flows into the first connection pipe 106 after passing through the bypass pipe 114.
- the intermediate-pressure liquid refrigerant reaches the meeting part 124b_all, passes through the electromagnetic valve 124b connected to the indoor unit D, passes through the second connection pipe 107d, and flows into the indoor unit D.
- the liquid refrigerant that has flowed into the indoor unit D is depressurized to a low pressure using the first flow rate regulator 109d that is controlled according to the degree of superheat at the outlet of the use side heat exchanger 105d of the indoor unit D. Then, the liquid refrigerant is supplied to the use side heat exchanger 105d in a state where the evaporation temperature is low. In the use side heat exchanger 105d, the supplied liquid refrigerant having a low evaporation temperature is evaporated and gasified by exchanging heat with a use medium such as air.
- the refrigerant that has become the gas refrigerant passes through the first connection pipe 106 d and flows into the first branching section 110.
- the flow volume adjustment valve 108a connected with the indoor unit D is opening. Therefore, the inflowing gas refrigerant passes through the flow rate adjustment valve 108a 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, flows into the heat source apparatus side heat exchanger 103, and evaporates into a gas state. Thereafter, the air is sucked into the compressor 101 through the four-way valve 102 and the accumulator 104.
- the first connection pipe 106 has a low pressure
- the second connection pipe 107 has a high pressure. Therefore, the refrigerant flows through the check valve 120 and the check valve 121 due to the pressure difference between the two pipes, but the refrigerant does not flow through the check valve 118 and the check valve 119. With the above operation, a refrigeration cycle is formed, and a heating main operation is performed.
- the refrigerant leaks in the indoor unit C or the indoor unit D during the simultaneous cooling and heating operation.
- the refrigerant moves from the relay unit B to the indoor unit C or the indoor unit D and leaks, the refrigerant flows down to the indoor side.
- coolant accumulates in a living room, the oxygen in a living room runs out.
- the risk of combustibility increases. As a result, the user who uses the air conditioning apparatus 1 not only becomes unpleasant, but also affects the body.
- the refrigerant leak When the refrigerant leaks in the indoor unit C or the indoor unit D, the refrigerant leak is detected by the refrigerant leak detector installed in the room in advance. And when a control part receives the signal, it is necessary to close an electromagnetic valve etc. and to interrupt
- an electromagnetic valve or the like is attached to each of the indoor unit C or the indoor unit D, not only a service space for the electromagnetic valve is required, but also a great cost is generated. Furthermore, in the state closed by the solenoid valve or the like, the pressure of the liquid refrigerant in the second connection pipes 107c and 107d increases, and the refrigerant may leak from the indoor unit C or the indoor unit D.
- the first connection pipes 106c and 106d and the second connection pipes 107c and 107d connected to the indoor unit C or the indoor unit D of the relay unit B are electromagnetically connected.
- the valves 108b and 124b or the flow rate adjusting valve 108a it is possible to suppress extra costs.
- the pressure relief valve 124a in parallel with the electromagnetic valve 124b, it is possible to achieve both suppression of excessive pressure rise and prevention of refrigerant leakage to the indoor unit C or the indoor unit D.
- the electromagnetic valves 108b and 124b or the flow rate adjusting valve 108a and the pressure relief valve 124a are shown as individually mounted. However, the present invention is not limited to this, and a plurality of these are mounted together. Also good.
- FIG. 4 is a diagram illustrating an example of the relationship between the flow coefficient CV value of the flow regulating valve 108a in the first branching unit 110 and the performance during cooling operation.
- FIG. 4 there is a certain correlation between the flow coefficient CV value of the flow regulating valve 108 a in the first branch 110 of the relay machine B and the indoor unit that is performing the cooling operation.
- the horizontal axis is the CV value of the flow rate adjustment valve 108a.
- the vertical axis is the capacity for cooling operation.
- the flow coefficient CV value of the flow regulating valve 108a in the first branch 110 is slightly opened like an orifice (for example, the CV value is 0.005 to 0.00). 15), it is possible to prevent liquid expansion due to liquid refrigerant remaining in the first connection pipes 106c and 106d. As a result, the pressure fluctuation during cooling operation is reduced by equalizing the pressure, and refrigerant flow noise is not generated.
- the heating capacity is significantly reduced. Therefore, in order to ensure the heating capability, the flow rate adjusting valve 108a and the electromagnetic valve 108b are provided and separated from each other, so that heat is not exchanged between the flow rate adjusting valve 108a and the electromagnetic valve 108b. The temperature of the gas refrigerant flowing into the operation side can be maintained.
- the following effects can be obtained by providing the first branch part 110 of the relay B with the electromagnetic valve 108b and the flow rate adjusting valve 108a, and providing the second branch part 111 with the electromagnetic valve 124b and the pressure relief valve 124a. can get.
- the pressure relief valve 124a is connected to the piping. Since the pressure of the refrigerant inside is reduced, the amount of refrigerant leaking is reduced, and the effect of suppressing the deterioration of the performance of the air conditioner 1 is obtained.
- the first connection is achieved by setting the flow coefficient CV value of the flow control valve 108a in the first branch 110 to a slightly opened state like an orifice. Liquid expansion due to the liquid refrigerant remaining in the pipes 106c and 106d can be prevented. As a result, the pressure fluctuation during cooling operation is reduced by equalizing the pressure, and the effect of suppressing refrigerant flow noise can be obtained. Furthermore, since the flow regulating valve 108a and the electromagnetic valve 108b, or the pressure relief valve 124a and the electromagnetic valve 124b are separately arranged, heat is not transferred between the valves, and the temperature of the gas refrigerant flowing into the heating operation side. Can be maintained. Thereby, the control of the safe and stable simultaneous cooling and heating operation can be simplified, and the effect of maintaining comfort at a low cost can be obtained.
- the air conditioning apparatus 1 shown in this Embodiment 1 has shown the example of the multi air conditioner etc. for buildings, for example, this invention is not limited to this.
- the switching valves (the flow regulating valve 108a and the electromagnetic valve 108b) provided in the first branch part 110 or the switching valves (the pressure relief valve 124a and the electromagnetic valve 124b) provided in the second branch part 111, By providing the airtight and vacuuming functions for performing the above operations, it becomes unnecessary to separately provide the airtight and vacuuming functions.
- FIG. 5 is a diagram illustrating an example of a switching valve having an airtight and vacuuming function.
- the switching valve flow rate adjustment valve 108 a and electromagnetic valve 108 b
- the airtight and vacuuming port 140 corresponds to the “airtight and vacuuming function” in the present invention.
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Abstract
Description
第二の目的は、暖房運転から冷房運転へ切り換えた場合、第1の接続配管に接続された弁の流量調整を行うことにより、冷媒流動音の発生を抑えることができる空気調和装置を得ることにある。
第三の目的は、冷暖房同時運転中、冷房運転または暖房運転を行っている利用側熱交換器が複数存在する場合であっても、性能を低下させることがなく、安価な材料で製造を可能とする空気調和装置を得ることにある。
図1は、空気調和装置の構成例を示す図である。本実施の形態1の空気調和装置は、例えばビル用マルチエアコンを例に説明する。図1に示されるように、空気調和装置1は、熱源機A、中継機B、室内機C及び室内機Dなどにより構成される。
中継機Bは、熱源機Aと室内機C及び室内機Dとの間に設けられている。中継機Bと熱源機Aは、第1の接続配管106と、第2の接続配管107とで接続されている。第2の接続配管107は第1の接続配管106に比べて配管径が細くなっている。
室内機Cと中継機Bは、第1の接続配管106cと、第2の接続配管107cとで接続されている。また、室内機Dと中継機Bは、第1の接続配管106dと、第2の接続配管107dとで接続されている。この接続構成で、中継機Bは、熱源機Aと室内機C及び室内機Dとの間を流れる冷媒を中継する。
なお、四方弁102は、本発明における「第1の切換弁」に相当する。
逆止弁118は、熱源機側熱交換器103及び逆止弁121の出口側と、第2の接続配管107及び逆止弁120の出口側との間に設けられている。逆止弁118の入口側は、熱源機側熱交換器103及び逆止弁121の出口側に接続された配管に接続されている。逆止弁118の出口側は、第2の接続配管107及び逆止弁120の出口側に接続された配管に接続される。逆止弁118は、熱源機側熱交換器103から第2の接続配管107への一方向からのみの冷媒の流通を許容する。
中継機Bは、第1の分岐部110、第2の分岐部111、気液分離器112、第2の流量調整器113、第3の流量調整器115、第1の熱交換器116、第2の熱交換器117、第1の圧力検出手段122、第2の圧力検出手段123、温度検出手段125、及び制御部151等を備える。
中継機Bは、第1の接続配管106及び第2の接続配管107を介して、熱源機Aと接続されている。中継機Bは、第1の接続配管106c及び第2の接続配管107cを介して、室内機Cと接続されている。中継機Bは、第1の接続配管106d及び第2の接続配管107dを介して、室内機Dと接続されている。
第1の分岐部110は、第1の接続配管106cを介して室内機Cと接続され、第1の接続配管106dを介して室内機Dと接続されている。
なお、第1の分岐部110は、流量調整弁108aと、電磁弁108bとを備える。流量調整弁108aと電磁弁108bは、第1の分岐部110内で分離された構成となっている。
室内機C側の流量調整弁108a及び電磁弁108bは、第1の接続配管106cを介して、室内機Cと接続されている。
室内機C側の流量調整弁108aは、一端が第1の接続配管106に接続され、他端が第1の接続配管106c及び電磁弁108bの一方の端子と接続されている。電磁弁108bの他の端子は第2の接続配管107に接続されている。なお、室内機C側の流量調整弁108aは、開閉可能かつ流量調整可能な弁である。
室内機D側の流量調整弁108a及び電磁弁108bは、第1の接続配管106dを介して、室内機Dと接続されている。
室内機D側の流量調整弁108aは、一端が第1の接続配管106に接続され、他端が第1の接続配管106d及び電磁弁108bの一方の端子と接続されている。電磁弁108bの他の端子は第2の接続配管107に接続されている。なお、室内機D側の流量調整弁108aは、開閉可能かつ流量調整可能な弁である。
第1の分岐部110は、第1の接続配管106及び第2の接続配管107を介して、熱源機Aと接続されている。
第1の分岐部110は、流量調整弁108a及び電磁弁108bを用いて、第1の接続配管106cを、第1の接続配管106又は第2の接続配管107に接続させる。同様に、第1の分岐部110は、流量調整弁108a及び電磁弁108bを用いて、第1の接続配管106dを、第1の接続配管106又は第2の接続配管107に接続させる。
なお、流量調整弁108a及び電磁弁108bは、本発明における「第2の切換弁」に相当する。
第2の分岐部111は、所定圧力以上の検知(例えば、設計圧力を超えないように設計圧力以下に設定する。)によって動作する圧力逃がし弁124aと、電磁弁124bとを備える。圧力逃がし弁124aと、電磁弁124bとは互いに逆並列関係に接続されている。
なお、圧力逃がし弁124a及び電磁弁124bは、本発明における「第3の切換弁」に相当する。また、圧力逃がし弁124aは、本発明における「所定圧力以上を検知して圧力を逃がす機能」に相当する。
また、第2の分岐部111は、第2の接続配管107dを介して室内機Dに接続されている。室内機D側の圧力逃がし弁124aの入力側及び電磁弁124bの出力側は、第2の接続配管107dを介して室内機Dに接続されている。
また、第2の分岐部111は、会合部124a_allを介して、第2の流量調整器113及び第2の熱交換器117に接続されている。さらに、第2の分岐部111は、会合部124b_allを介して、第3の流量調整器115及び第2の熱交換器117に接続されている。
気液分離器112は、第2の接続配管107の途中に設けられている。気液分離器112の気相部は、第1の分岐部110の電磁弁108bに接続されている。また、気液分離器112の液相部は、第1の熱交換器116、第2の流量調整器113、第2の熱交換器117、及び第3の流量調整器115を介して、第2の分岐部111に接続されている。
第2の流量調整器113は、開度が調整可能な流量調整器であり、第1の圧力検出手段122で検出した圧力値と、第2の圧力検出手段123で検出した圧力値との差が一定となるように開度を調整する。
第3の流量調整器115は、開度が調整可能な流量調整器であり、温度検出手段125、第1の圧力検出手段122及び第2の圧力検出手段123の何れか、又はその複数の組み合わせにより開度を調整する。なお、バイパス配管114は、一端が第1の接続配管106に接続され、他端が第3の流量調整器115に接続されている。このため、第3の流量調整器115の開度に応じて、熱源機Aへ供給される冷媒の量は変動する。
なお、上記の説明では、温度検出手段125は、サーミスタで形成される例について説明したが、本発明はこれに限定されない。
第2の圧力検出手段123は、第2の流量調整器113と、第2の熱交換器117及び第2の分岐部111との間に設けられた配管内を流れる冷媒の圧力を測定し、測定結果を制御部151に供給する。
第2の流量調整器113の開度は、第1の圧力検出手段122と第2の圧力検出手段123との差圧が適度な値になるように制御される。
熱源機側熱交換器103内を通過する冷媒は、水等の熱源媒体と熱交換される。熱交換された高温高圧のガス冷媒は、気液二相の高温高圧の冷媒となる。次に、気液二相の高温高圧の冷媒は、逆止弁118を経て、第2の接続配管107を通過し、中継機Bの気液分離器112へ供給される。
第1の流量調整器109dは、利用側熱交換器105dで凝縮液化された液冷媒を減圧し、高圧と低圧との中間の圧力である中間圧の冷媒にする。中間圧となった冷媒は、圧力逃がし弁124aを通過し、第2の分岐部111に流入する。
次に、第2の分岐部111では、供給された液状冷媒は、室内機C側に接続されている電磁弁124bを通過し、室内機Cへ流入する。
次に、流入した液状冷媒は、室内機Cの利用側熱交換器105cの出口の過熱度に応じて制御される第1の流量調整器109cによって低圧まで減圧された後、利用側熱交換器105cに供給される。
ここで、第1の分岐部110において、室内機Cと接続されている流量調整弁108aは開口している。そこで、流入したガス冷媒は、室内機Cと接続されている流量調整弁108aを通過し、第1の接続配管106へ流入する。
次に、ガス冷媒は、逆止弁121よりも低圧の逆止弁119側へ流入する。その後、ガス冷媒は、四方弁102、アキュムレータ104を経て、圧縮機101へ吸入される。
以上の動作で、冷凍サイクルが形成され、冷房主体運転が行われる。
第2の流量調整器113の開度は、第1の圧力検出手段122と第2の圧力検出手段123との差圧が適度な値になるように制御される。
気液分離器112は、高温高圧のガス冷媒を、第1の分岐部110へ供給する。第1の分岐部110へ供給されたガス冷媒は、室内機C側の開口している電磁弁108b及び第1の接続配管106cを経て、暖房運転が設定されている室内機Cへ供給される。
第1の流量調整器109cは、利用側熱交換器105cで凝縮液化された液冷媒を減圧し、高圧と低圧との中間の圧力である中間圧の液冷媒にする。中間圧となった液冷媒は、圧力逃がし弁124aを通過し、第2の分岐部111に流入する。
利用側熱交換器105dでは、供給された蒸発温度の低い液状冷媒は、空気等の利用媒体と熱交換することで、蒸発してガス化する。
次に、ガス冷媒は、逆止弁119よりも低圧の逆止弁121側へ流入し、熱源機側熱交換器103に流入して蒸発してガス状態となる。その後、四方弁102、アキュムレータ104を経て、圧縮機101へ吸入される。
以上の動作で、冷凍サイクルが形成され、暖房主体運転が行われる。
さらに、電磁弁等で閉止した状態では、第2の接続配管107c、107d内の液状冷媒の圧力が上昇し、室内機Cもしくは室内機Dから冷媒が漏れる可能性がある。
さらに、電磁弁124bと並列に圧力逃がし弁124aを取付けることで、過剰な圧力上昇の抑制と室内機Cもしくは室内機Dへ冷媒漏えいの防止を両立することができる。
図4は、第1の分岐部110内の流量調整弁108aの流量係数CV値と冷房運転時の性能との関係の例を示す図である。図4に示されるように、中継機Bの第1の分岐部110内の流量調整弁108aの流量係数CV値と、冷房運転している室内機とは、一定の相関関係が存在する。横軸が流量調整弁108aのCV値であると想定する。また、縦軸が冷房運転している能力と想定する。
したがって、室内機側で冷媒が漏れても、性能低下することなく、安全かつ安定した冷暖房同時運転を継続させることができる。
暖房運転している室内機に流入するガス冷媒の圧力及び温度が低下すると、室内機C又は室内機Dから吹き出される空気等の利用媒体の温度が低下する。この結果、空気調和装置1を利用するユーザーは不快な状態になる。
そこで、暖房能力を確保するために、流量調整弁108aと電磁弁108bを各々設け、分離して配置することで、流量調整弁108aと電磁弁108bとの間で熱の授受が無くなるため、暖房運転側に流入するガス冷媒の温度を維持することができる。上記は第1の分岐部110について説明したが、第2の分岐部111も同様の効果を奏する。
冷暖房同時運転中に、冷房運転もしくは暖房運転を行っている利用側熱交換器105c等が複数存在する場合に、室内機C又は室内機D側で冷媒が漏れても、圧力逃がし弁124aが配管内の冷媒の圧力を減圧するため、冷媒の漏れる量が減少し、空気調和装置1の性能の低下を抑える効果が得られる。
また、暖房運転から冷房運転へ変化した場合でも、第1の分岐部110内の流量調整弁108aの流量係数CV値をオリフィスのように僅かに開口された状態にすることで、第1の接続配管106c、106d内に液状冷媒が滞留することによる液膨張を防止できる。これにより、均圧されることで冷房運転時の圧力変動が小さくなり、冷媒流動音を抑える効果が得られる。
さらに、流量調整弁108a及び電磁弁108b、又は圧力逃がし弁124a及び電磁弁124bが分離して配置されることで、弁の間で熱の授受が無くなり、暖房運転側に流入するガス冷媒の温度を維持することができる。これにより、安全かつ安定した冷暖房同時運転の制御を簡易にし、低コストで快適性を保つ効果が得られる。
図5に示されるように、第1の分岐部110に設けられた切換弁(流量調整弁108a及び電磁弁108b)には、気密及び真空引きポート140が設けられている。
なお、気密及び真空引きポート140は、本発明における「気密及び真空引き機能」に相当する。
Claims (7)
- 冷媒を圧縮して吐出する圧縮機と、前記圧縮機から吐出された前記冷媒の流路を切り換える第1の切換弁と、前記第1の切換弁を通過した前記冷媒と周囲の熱源媒体とで熱交換をする熱源機側熱交換器と、を搭載した熱源機と、
前記第1の切換弁を通過した前記冷媒と周囲の利用媒体とで熱交換をする利用側熱交換器と、前記利用側熱交換器に接続された流量調整器と、をそれぞれ搭載した複数台の室内機と、
前記熱源機と前記室内機との間に設けられ、前記熱源機と前記各室内機とを第1の接続配管及び第2の接続配管を介して接続し、前記複数台の室内機の利用側熱交換器の一部を冷房運転側に切り換え、前記利用側熱交換器の他の一部を暖房運転側に切り換える機能を備える中継機と、
を備えた空気調和装置であって、
前記中継機は、
前記利用側熱交換器を冷房運転側又は暖房運転側に切り換え可能に接続する第2の切換弁を有し、前記第2の切換弁を第1の接続配管に接続させる第1の分岐部と、
前記流量調整器にそれぞれ接続された第3の切換弁を有し、前記第3の切換弁を第2の接続配管に接続させる第2の分岐部と、
を備え、
前記第2の分岐部に設けられた第3の切換弁は、所定圧力以上を検知して圧力を逃がす機能を有する、
空気調和装置。 - 前記第1の分岐部に設けられた第2の切換弁は、
冷房運転側に接続された弁と、暖房運転側に接続された弁とを有し、
前記冷房運転側に接続された弁は、流量調整弁からなる、
請求項1に記載の空気調和装置。 - 前記流量調整弁は、暖房運転から冷房運転へ切り換える際に、所定開度まで開口されるようにした
請求項1又は2に記載の空気調和装置。 - 前記第1の分岐部に設けられた第2の切換弁は、冷房運転側に接続された弁と、暖房運転側に接続された弁とが分離して配置された
請求項1~3の何れか一項に記載の空気調和装置。 - 前記流量調整弁は、流量係数CV値4.0以下の範囲で流量調整可能とする
請求項2に記載の空気調和装置。 - 前記第1の分岐部の第2の切換弁及び前記第2の分岐部の第3の切換弁の少なくとも一方の切換弁は、熱電導率が150[W/mK]~200[W/mK]の材料で成形された
請求項1~5の何れか一項に記載の空気調和装置。 - 前記第1の分岐部の第2の切換弁及び前記第2の分岐部の第3の切換弁のいずれか一方の切換弁は、前記室内機又は前記接続配管内に対する気密及び真空引き機能を有する
請求項1~6の何れか一項に記載の空気調和装置。
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JP2016520870A JP6198945B2 (ja) | 2014-05-21 | 2014-05-21 | 空気調和装置 |
PCT/JP2014/063520 WO2015177896A1 (ja) | 2014-05-21 | 2014-05-21 | 空気調和装置 |
GB1621859.6A GB2542301B (en) | 2014-05-21 | 2014-05-21 | Air conditioning apparatus |
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PCT/JP2014/063520 WO2015177896A1 (ja) | 2014-05-21 | 2014-05-21 | 空気調和装置 |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN110701726A (zh) * | 2018-07-10 | 2020-01-17 | 奥克斯空调股份有限公司 | 一种空调冷媒泄露的检测方法 |
WO2023223539A1 (ja) * | 2022-05-20 | 2023-11-23 | 三菱電機株式会社 | 空気調和装置 |
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JPH06147674A (ja) * | 1992-11-06 | 1994-05-27 | Matsushita Refrig Co Ltd | 多室型空気調和機 |
JP2003172538A (ja) * | 2001-12-06 | 2003-06-20 | Mitsubishi Electric Corp | 空気調和機の制御装置及び空気調和機 |
JP2010261713A (ja) * | 2010-07-23 | 2010-11-18 | Mitsubishi Electric Corp | 空気調和装置 |
WO2011089637A1 (ja) * | 2010-01-19 | 2011-07-28 | 三菱電機株式会社 | 空調給湯複合システム |
-
2014
- 2014-05-21 GB GB1621859.6A patent/GB2542301B/en active Active
- 2014-05-21 JP JP2016520870A patent/JP6198945B2/ja active Active
- 2014-05-21 WO PCT/JP2014/063520 patent/WO2015177896A1/ja active Application Filing
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH06147674A (ja) * | 1992-11-06 | 1994-05-27 | Matsushita Refrig Co Ltd | 多室型空気調和機 |
JP2003172538A (ja) * | 2001-12-06 | 2003-06-20 | Mitsubishi Electric Corp | 空気調和機の制御装置及び空気調和機 |
WO2011089637A1 (ja) * | 2010-01-19 | 2011-07-28 | 三菱電機株式会社 | 空調給湯複合システム |
JP2010261713A (ja) * | 2010-07-23 | 2010-11-18 | Mitsubishi Electric Corp | 空気調和装置 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN110701726A (zh) * | 2018-07-10 | 2020-01-17 | 奥克斯空调股份有限公司 | 一种空调冷媒泄露的检测方法 |
CN110701726B (zh) * | 2018-07-10 | 2021-05-18 | 奥克斯空调股份有限公司 | 一种空调冷媒泄露的检测方法 |
WO2023223539A1 (ja) * | 2022-05-20 | 2023-11-23 | 三菱電機株式会社 | 空気調和装置 |
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JP6198945B2 (ja) | 2017-09-20 |
GB201621859D0 (en) | 2017-02-01 |
JPWO2015177896A1 (ja) | 2017-04-20 |
GB2542301A (en) | 2017-03-15 |
GB2542301B (en) | 2020-06-17 |
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