WO2016207947A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2016207947A1 WO2016207947A1 PCT/JP2015/067868 JP2015067868W WO2016207947A1 WO 2016207947 A1 WO2016207947 A1 WO 2016207947A1 JP 2015067868 W JP2015067868 W JP 2015067868W WO 2016207947 A1 WO2016207947 A1 WO 2016207947A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat exchanger
- compressor
- unit
- blower
- Prior art date
Links
Images
Classifications
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/24—Means for preventing or suppressing noise
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/40—Vibration or noise prevention at outdoor units
-
- 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
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
-
- 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
- F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
- F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2221/00—Details or features not otherwise provided for
- F24F2221/54—Heating and cooling, simultaneously or alternatively
Definitions
- the present invention relates to an air conditioner in which a plurality of outdoor units are connected to an indoor unit through one refrigerant system, and more particularly to an air conditioner that equalizes the refrigerant amount of each outdoor unit.
- air conditioners equipped with a plurality of outdoor units have been developed.
- an air conditioner including a plurality of outdoor units there may be a refrigerant bias between the outdoor units due to various factors. Therefore, conventionally, an air conditioner has been proposed that corrects (evens out) the refrigerant bias occurring between the outdoor units.
- an air conditioner described in Patent Document 1 includes a plurality of outdoor units equipped with a compressor, a four-way switching valve, a heat exchanger, and an accumulator, and calculates the degree of superheat of the refrigerant flowing out of the heat exchanger.
- the heat exchanger outlet superheat degree calculating means and the compressor discharge superheat degree calculating means for calculating the superheat degree of the refrigerant discharged from the compressor are provided.
- the air conditioner determines an imbalance in the amount of liquid refrigerant in the accumulator based on the calculated values of the heat exchanger outlet superheat degree calculating means and the compressor discharge superheat degree calculating means, and executes liquid equalization control.
- Liquid equalization control means is provided.
- the air conditioner is provided with a blower for supplying air to the heat exchanger in the outdoor unit, and the liquid leveling control means includes a heat exchanger outlet superheat degree calculating means and a compressor discharge superheat degree calculating means.
- the operation output of the blower is controlled based on the calculated value.
- the liquid leveling control means of the air conditioner converges the superheat degree of the refrigerant flowing out of the heat exchanger and the superheat degree of the refrigerant discharged from the compressor to a preset reference value. Control is being executed.
- liquid leveling control is performed using a blower for supplying air to the heat exchanger.
- the liquid leveling control means of the air conditioner performs the liquid leveling control by decreasing the air volume of one blower of the air conditioners connected to two or more units and increasing the air volume of the other fan. Yes.
- the liquid leveling control it is necessary to increase the air volume of one blower from the normal time depending on the load applied to the air conditioner.
- the noise of the outdoor unit increases when the air volume of one blower is increased from the normal time, in order to avoid this, it is necessary to further reduce the air volume of the other blower.
- the present invention has been made to solve the above-described problems, and it is an object of the present invention to obtain an air conditioner that suppresses an increase in the noise of a blower of an outdoor unit when equalizing the refrigerant amount of each outdoor unit. Objective.
- An air conditioner according to the present invention is an air conditioner including a plurality of outdoor units equipped with a compressor, a heat source side heat exchanger, and a blower, and an indoor unit equipped with an indoor side heat exchanger.
- the plurality of outdoor units are obtained from a first superheat degree of the refrigerant flowing out from the heat source side heat exchanger and a second superheat degree of the refrigerant discharged from the compressor.
- the operation output of the outdoor unit blower with the larger refrigerant amount is increased, and the operation output of the outdoor unit blower with the smaller refrigerant amount is decreased.
- a control unit that performs liquid leveling control, and the control unit operates the blower normally when the outdoor temperature is higher than a reference temperature and the operation capacity of the indoor unit is less than the reference capacity.
- the operation output of the blower during normal operation is The liquid leveling control is executed by increasing the maximum value.
- the control unit when the outdoor temperature is greater than a predetermined value and the operation capacity of the indoor unit is less than the predetermined value, the control unit sets the blower to an operation output during normal operation and performs liquid leveling control.
- the outdoor temperature is lower than a predetermined value, or when the outdoor temperature is higher than a predetermined value and the operating capacity of the indoor unit is higher than a predetermined value, the fan is operated based on the operation output during normal operation. Increase the liquid leveling control.
- FIG. 1 is a schematic refrigerant circuit diagram of an air conditioner according to an embodiment of the present invention. It is a refrigerant circuit figure at the time of the heating operation of the air conditioning apparatus which concerns on embodiment of this invention. It is a flowchart which concerns on control operation of the control part at the time of the heating operation of the air conditioning apparatus which concerns on embodiment of this invention.
- FIG. 1 is a schematic refrigerant circuit diagram of an air-conditioning apparatus according to an embodiment of the present invention. Based on FIG. 1, the structure of the refrigerant circuit of the air conditioning apparatus 500 is demonstrated.
- the air conditioner 500 performs a cooling operation and a heating operation using a refrigeration cycle (heat pump cycle) for circulating a refrigerant.
- the air conditioner 500 includes an outdoor unit 51 and an outdoor unit 151 as heat source side units, and includes an indoor unit 53a and an indoor unit 53b as load side units.
- the outdoor unit 51 and the outdoor unit 151 are connected to the flow dividing controller 52 by the low pressure pipe 201 and the high pressure pipe 202, and further connected in parallel to the indoor unit 53a and the indoor unit 53b from the flow dividing controller 52 to constitute a refrigeration cycle circuit. Yes.
- the air conditioning apparatus 500 is provided with the control part 20 mentioned later. Note that the air conditioner 500 illustrated in FIG. 1 is merely an example, and may include three or more outdoor units, or one or three or more indoor units.
- the outdoor unit 51 includes a compressor 1, a heat source side heat exchanger 2, a four-way valve 3, an accumulator 4, check valves 5a, 5b, 5c, and 5d and a blower 6.
- the outdoor unit 51 includes a high pressure detection unit 31, a low pressure detection unit 32, a compressor discharge temperature detection unit 34, a heat exchanger outlet temperature detection unit 35, an outside air temperature detection unit 36, and a compressor discharge superheat degree calculation unit 37.
- the heat exchanger outlet superheat degree calculating means 38 and the indoor unit operating capacity calculating means 41 are provided.
- the compressor 1 sucks the refrigerant and compresses the refrigerant to a high temperature and high pressure state.
- a four-way valve 3 is connected to the discharge side of the compressor 1.
- the four-way valve 3 switches the flow path of the refrigerant discharged from the compressor 1 to a flow path that flows to the heat source side heat exchanger 2 or a flow path that flows to the indoor unit 53a and the indoor unit 53b.
- the four-way valve 3 is also connected to the accumulator 4 so that the refrigerant flowing from the heat source side heat exchanger 2 or the indoor unit 53a and the indoor unit 53b is sent to the accumulator 4.
- the four-way valve is exemplified as the flow path switching valve.
- the present invention is not limited to this, and for example, a two-way valve or a three-way valve may be combined.
- the blower 6 is composed of a fan or the like and has a function for blowing air to the heat source side heat exchanger 2.
- the accumulator 4 stores excess refrigerant, and is a container that can store excess refrigerant.
- the accumulator 4 does not need to be provided depending on the usage condition of the air conditioning apparatus 500.
- the outdoor unit 151 includes a compressor 101, a heat source side heat exchanger 102, a four-way valve 103, an accumulator 104, check valves 105 a, 105 b, 105 c, and 105 d and a blower 106, similar to the compressor 1.
- the outdoor unit 151 includes a high pressure detection unit 131, a low pressure detection unit 132, a compressor discharge temperature detection unit 134, a heat exchanger outlet temperature detection unit 135, an outside air temperature detection unit 136, and a compressor discharge superheat degree calculation unit 137.
- the heat exchanger outlet superheat degree calculating means 138 and the indoor unit operating capacity calculating means 141 are provided.
- the compressor 101 sucks the refrigerant and compresses the refrigerant to a high temperature and high pressure state.
- a four-way valve 103 is connected to the discharge side of the compressor 101.
- the four-way valve 103 switches the flow path of the refrigerant discharged from the compressor 101 to a flow path that flows to the heat source side heat exchanger 102, or a flow path that flows to the indoor unit 53a and the indoor unit 53b.
- the four-way valve 103 is also connected to the accumulator 104 so that the refrigerant flowing from the heat source side heat exchanger 102 or the indoor unit 53a and the indoor unit 53b is sent to the accumulator 104.
- the four-way valve is exemplified as the flow path switching valve.
- the present invention is not limited to this, and for example, a two-way valve or a three-way valve may be combined.
- the blower 106 is configured by a fan or the like, and has a function for blowing air to the heat source side heat exchanger 102.
- the accumulator 104 stores excess refrigerant and is a container that can store excess refrigerant.
- the accumulator 104 may not be provided depending on the use mode of the air conditioner 500.
- the four-way valve 3 and the four-way valve 103 perform valve switching corresponding to the mode (mode) of the air conditioning operation so that the refrigerant path is switched.
- mode mode
- the cooling only operation referred to here as the operation when all the indoor units performing air conditioning are cooling
- the cooling main operation of the simultaneous cooling and heating operation
- the cooling load is Large operation
- heating operation here, operation when all air-conditioned indoor units are heating
- heating operation heating and cooling among simultaneous heating and cooling operations
- the heat source side heat exchanger 2 and the heat source side heat exchanger 102 have heat transfer tubes that allow the refrigerant to pass therethrough and fins for increasing the heat transfer area between the refrigerant flowing through the heat transfer tubes and the outside air, Exchange heat with air (outside air).
- it functions as an evaporator during the heating only operation or during the heating main operation, and evaporates the refrigerant, for example.
- it functions as a condenser during the cooling only operation or during the cooling main operation, for example, condenses and liquefies the refrigerant.
- adjustment is performed such as condensing to a state of two-phase mixing (gas-liquid two-phase state) of liquid and gas, instead of being completely gasified or liquefied, for example, at the time of cooling main operation. .
- the air conditioner 500 includes an outdoor unit 51, an outdoor unit 151, an indoor unit 53a, an indoor unit 53b, and a shunt controller 52.
- a shunt controller 52 is provided between the outdoor unit 51, the outdoor unit 151 and the indoor unit 53a, and the indoor unit 53b, and piping between these devices is made by various refrigerant pipes. Connecting. Further, the plurality of indoor units 53a and 53b are connected so as to be parallel to each other. For example, in the indoor unit 53a, the indoor unit 53b, and the like, when there is no need to particularly distinguish or specify, the a and b suffixes are omitted and referred to as the indoor unit 53.
- the example which provided the shunt controller 52 in the air conditioning apparatus 500 in this Embodiment was shown, depending on the usage condition of the air conditioning apparatus 500, it is not necessary to provide the shunt controller 52.
- the outdoor unit 51, the outdoor unit 151, and the shunt controller 52 are connected by a low pressure pipe 201 and a high pressure pipe 202.
- a refrigerant branch point 19 is provided between the outdoor unit 51 and the outdoor unit 151 and the low pressure pipe 201 to branch the refrigerant from the low pressure pipe 201 and guide the refrigerant to the outdoor unit 51 and the outdoor unit 151.
- a refrigerant junction 18 is provided between the outdoor unit 51 and the outdoor unit 151 and the high-pressure pipe 202 to join the refrigerant from the outdoor unit 51 and the outdoor unit 151 and guide the refrigerant to the high-pressure pipe 202.
- high-pressure refrigerant flows from the outdoor unit 51 and outdoor unit 151 side to the shunt controller 52 side.
- a refrigerant having a pressure lower than that flowing through the high-pressure pipe 202 flows from the shunt controller 52 side to the outdoor unit 51 and the outdoor unit 151.
- the level of the pressure is not determined by the relationship with the reference pressure (numerical value), but the pressurization of the compressor 1 and the compressor 101 and the opening / closing of each throttle device (flow rate limiting device) ( It is assumed that it is expressed based on relative elevation (including the middle) in the refrigerant circuit by controlling the (opening) state.
- the shunt controller 52 and the indoor unit 53a are connected by a liquid pipe 203a and a gas pipe 204a.
- the indoor unit 53b is connected by a liquid pipe 203b and a gas pipe 204b.
- the liquid pipe 203 when not distinguishing especially the liquid pipe 203a and the liquid pipe 203b, it will be called the liquid pipe 203.
- the gas pipe 204 when not distinguishing especially the gas pipe 204a and the gas pipe 204b, it will be called the gas pipe 204.
- the refrigerant circulates between the outdoor unit 51, the outdoor unit 151, the shunt controller 52, and the indoor unit 53, thereby forming a refrigerant circuit.
- the check valves 5a, 5b, 5c, and 5d of the outdoor unit 51 prevent the refrigerant from flowing back, regulate the flow of the refrigerant, and make the refrigerant circulation path constant according to the operation mode.
- the check valve 5 a is located on the pipe between the four-way valve 3 and the low-pressure pipe 201, and allows the refrigerant flow from the low-pressure pipe 201 toward the four-way valve 3.
- the check valve 5 b is located on the pipe between the heat source side heat exchanger 2 and the low pressure pipe 201 and allows the refrigerant flow from the low pressure pipe 201 toward the heat source side heat exchanger 2.
- the check valve 5 c is located on the pipe between the four-way valve 3 and the high-pressure pipe 202 and allows the refrigerant flow from the four-way valve 3 to the high-pressure pipe 202.
- the check valve 5 d is located on the pipe between the heat source side heat exchanger 2 and the high pressure pipe 202 and allows the refrigerant flow from the heat source side heat exchanger 2 toward the high pressure pipe 202.
- the check valves 105a, 105b, 105c, and 105d of the outdoor unit 151 prevent the refrigerant from flowing backward, regulate the flow of the refrigerant, and make the circulation path of the refrigerant consistent with the mode.
- the check valve 105 a is located on the pipe between the four-way valve 103 and the low-pressure pipe 201, and allows the refrigerant flow from the low-pressure pipe 201 toward the four-way valve 103.
- the check valve 105 b is located on the pipe between the heat source side heat exchanger 102 and the low pressure pipe 201 and allows the refrigerant flow from the low pressure pipe 201 toward the heat source side heat exchanger 102.
- the check valve 105 c is located on the pipe between the four-way valve 103 and the high-pressure pipe 202 and allows the refrigerant flow from the four-way valve 103 to the high-pressure pipe 202.
- the check valve 105 d is located on a pipe between the heat source side heat exchanger 102 and the high pressure pipe 202, and allows the refrigerant flow from the heat source side heat exchanger 102 to the high pressure pipe 202.
- a high pressure detecting means 31 for detecting the pressure of the refrigerant is attached on the discharge side of the compressor 1, and on the suction side of the compressor 1, on the outlet side of the heat source side heat exchanger 2 during heating operation.
- Low pressure detection means 32 for detecting the pressure of the refrigerant is attached.
- the outdoor unit 51 is provided with a compressor discharge temperature detecting means 34 for detecting the temperature of the refrigerant on the high pressure side (discharge side) of the compressor 1.
- the outdoor unit 51 is provided with heat exchanger outlet temperature detection means 35 for detecting the temperature of the refrigerant on the outlet side of the heat source side heat exchanger 2 during the heating operation.
- the outdoor unit 51 is provided with an outside air temperature detecting means 36 that detects the outside air temperature around the outdoor unit 51.
- the high pressure detection means 31 and the low pressure detection means 32 are constituted by a pressure sensor or the like.
- the compressor discharge temperature detection means 34, the heat exchanger outlet temperature detection means 35, and the outside air temperature detection means 36 are constituted by temperature sensors such as a thermistor.
- the outdoor unit 51 includes a compressor discharge superheat degree calculation means 37, a heat exchanger outlet superheat degree calculation means 38, and an indoor unit operation capacity calculation means 41, which are constituted by, for example, a microcomputer.
- the compressor discharge superheat degree calculation means 37 calculates the superheat degree of the refrigerant discharged from the compressor 1.
- the heat exchanger outlet superheat degree calculation means 38 calculates the superheat degree of the refrigerant flowing out from the heat source side heat exchanger 2.
- the indoor unit operating capacity calculating means 41 calculates the operating capacity of the indoor unit 53.
- the outdoor unit 51 is connected to the control unit 20 described later.
- the control unit 20 is configured by a microcomputer, for example.
- the outdoor unit 51 is provided with the compressor discharge superheat degree calculation means 37, the heat exchanger outlet superheat degree calculation means 38, and the indoor unit operating capacity calculation means 41.
- the invention is not limited to this, and a computing unit in which the above computing units are combined into one may be provided, or a computing unit may be provided separately.
- a high pressure detecting means 131 for detecting the pressure of the refrigerant is mounted on the discharge side pipe of the compressor 101, and on the suction side pipe of the compressor 101, on the outlet side of the heat source side heat exchanger 102 during heating operation.
- Low pressure detection means 132 for detecting the pressure of the refrigerant is attached.
- the outdoor unit 151 is provided with a compressor discharge temperature detecting means 134 for detecting the temperature of the refrigerant on the high pressure side (discharge side) of the compressor 101.
- the outdoor unit 151 is provided with heat exchanger outlet temperature detection means 135 for detecting the temperature of the refrigerant on the outlet side of the heat source side heat exchanger 102 during the heating operation.
- the outdoor unit 151 is provided with an outside air temperature detection unit 136 that detects the outside air temperature around the outdoor unit 151.
- the high pressure detection means 131 and the low pressure detection means 132 are constituted by pressure sensors or the like.
- the compressor discharge temperature detection means 134, the heat exchanger outlet temperature detection means 135, and the outside air temperature detection means 136 are constituted by temperature sensors such as a thermistor.
- the outdoor unit 151 includes a compressor discharge superheat degree calculation means 137, a heat exchanger outlet superheat degree calculation means 138, and an indoor unit operation capacity calculation means 141, which are constituted by a microcomputer, for example.
- the compressor discharge superheat degree calculation means 137 calculates the superheat degree of the refrigerant discharged from the compressor 101.
- the heat exchanger outlet superheat degree calculation means 138 calculates the superheat degree of the refrigerant flowing out from the heat source side heat exchanger 102.
- the indoor unit operating capacity calculating means 141 calculates the operating capacity of the indoor unit 53.
- the outdoor unit 151 is connected to a control unit 20 described later.
- the outdoor unit 151 is provided with the compressor discharge superheat degree calculation means 137, the heat exchanger outlet superheat degree calculation means 138, and the indoor unit operating capacity calculation means 141.
- the invention is not limited to this, and a computing unit in which the above computing units are combined into one may be provided, or a computing unit may be provided separately.
- the gas-liquid separator 11 included in the shunt controller 52 separates the refrigerant flowing from the high pressure pipe 202 into a gas refrigerant and a liquid refrigerant.
- a gas phase portion (not shown) through which the gas refrigerant flows is connected to the electromagnetic valve 12a and the electromagnetic valve 12b.
- the liquid phase part (not shown) from which the liquid refrigerant flows is connected to the inter-refrigerant heat exchanger 16.
- the solenoid valve 12a, solenoid valve 12b, solenoid valve 13a, and solenoid valve 13b in the shunt controller open and close based on the operation mode.
- One end of the electromagnetic valve 12a is connected to the gas-liquid separator 11, and the other end is connected to the gas pipe 204a.
- One end of the electromagnetic valve 12b is connected to the gas-liquid separator 11, and the other end is connected to 204b.
- one end of the electromagnetic valve 13a is connected to the gas pipe 204a, and the other end is connected to the low pressure pipe 201.
- One end of the electromagnetic valve 13b is connected to 204b, and the other end is connected to the low pressure pipe 201.
- the refrigerant flows from the indoor unit 53 side to the low pressure pipe 201 side based on the operation mode, or the gas-liquid separator 11 side
- the valve is switched so that the refrigerant flows from to the indoor unit 53 side.
- the flow of the refrigerant is switched by the electromagnetic valve 12a, the electromagnetic valve 12b, the electromagnetic valve 13a, and the electromagnetic valve 13b.
- a three-way valve or the like may be used.
- the expansion device 14 is provided between the inter-refrigerant heat exchanger 16 and the inter-refrigerant heat exchanger 17, controls the opening degree based on the operation mode of the cooling operation and the heating operation, and flows from the gas-liquid separator 11. Adjust the flow rate and refrigerant pressure. On the other hand, the expansion device 15 controls the opening and adjusts the refrigerant flow rate and the refrigerant pressure. As will be described later, the refrigerant that has passed through the expansion device 15 supercools the refrigerant flowing through the refrigerant heat exchanger 17 and the refrigerant heat exchanger 16 in the refrigerant heat exchanger 17 and the refrigerant heat exchanger 16, It flows to the low pressure pipe 201. It is assumed that the expansion device 14 and the expansion device 15 are composed of, for example, an electronic expansion valve that can change the opening degree.
- the inter-refrigerant heat exchanger 17 performs heat exchange between the refrigerant in the downstream portion of the expansion device 15 (the refrigerant that has passed through the expansion device 15) and the refrigerant that flows from the expansion device 14.
- the inter-refrigerant heat exchanger 16 exchanges heat between the refrigerant that has passed through the inter-refrigerant heat exchanger 17 and the liquid refrigerant that flows from the gas-liquid separator 11 toward the expansion device 14.
- the indoor unit 53a includes an indoor side heat exchanger 22a and an indoor side expansion device 23a connected in series in proximity to the indoor side heat exchanger 22a.
- the indoor side heat exchanger 22a serves as an evaporator during the cooling operation and serves as a condenser during the heating operation, and between the air and the refrigerant in the air-conditioning target space. Perform heat exchange.
- a blower for efficiently performing heat exchange between the refrigerant and the air may be provided in the vicinity of each indoor heat exchanger 22a.
- the indoor unit 53b includes an indoor side heat exchanger 22b and an indoor side expansion device 23b connected in series in proximity to the indoor side heat exchanger 22b.
- the indoor side heat exchanger 22b serves as an evaporator during the cooling operation and serves as a condenser during the heating operation, and between the air and the refrigerant in the air-conditioning target space. Perform heat exchange.
- a blower for efficiently performing heat exchange between the refrigerant and the air may be provided in the vicinity of each indoor heat exchanger 22b.
- the indoor side heat exchanger 22a and the indoor side heat exchanger 22b are not particularly distinguished, they are referred to as the indoor side heat exchanger 22, and similarly, the indoor side expansion device 23a and the indoor side expansion device 23b are not particularly distinguished. In this case, it is referred to as an indoor expansion device 23.
- the indoor expansion device 23 functions as a pressure reducing valve or an expansion valve, and adjusts the pressure of the refrigerant passing through the indoor heat exchanger 22.
- the indoor side expansion device 23 is composed of, for example, an electronic expansion valve that can change the opening degree.
- the opening degree of the indoor expansion device 23 is determined based on the degree of superheat on the refrigerant outlet side (here, the gas pipe 204 side) of the indoor heat exchanger 22 during the cooling operation. Further, it is determined based on the degree of supercooling on the refrigerant outlet side (here, on the liquid pipe 203 side) during the heating operation.
- the air-conditioning apparatus 500 of the present embodiment configured as described above performs the operation in any one of the four modes (modes) of the cooling only operation, the heating only operation, the cooling main operation, and the heating main operation. It can be carried out.
- FIG. 2 is a refrigerant circuit diagram during heating operation of the air-conditioning apparatus according to the embodiment of the present invention.
- the flow of the refrigerant during the all heating operation is indicated by solid arrows in FIG.
- the compressor 1 compresses the sucked refrigerant and discharges a high-pressure gas refrigerant.
- the refrigerant discharged from the compressor 1 flows through the four-way valve 3 and the check valve 5c (does not flow toward the check valve 5a and the check valve 5d), passes through the refrigerant confluence 18 and passes through the high-pressure pipe 202. Flow into the diversion controller 52.
- the compressor 101 compresses the sucked refrigerant and discharges the high-pressure gas refrigerant.
- the refrigerant discharged from the compressor 101 flows through the four-way valve 103 and the check valve 105c (does not flow toward the check valve 105a and the check valve 105d). Then, the refrigerant merges with the refrigerant that has flowed out of the outdoor unit 51 at the refrigerant merge point 18, and flows into the diversion controller 52 through the high-pressure pipe 202.
- the solenoid valve 12a and the solenoid valve 12b are opened, and the solenoid valve 13a and the solenoid valve 13b are closed.
- Part of the gas refrigerant that has flowed into the shunt controller 52 passes through the gas-liquid separator 11, the electromagnetic valve 12a, and the gas pipe 204a, and flows into the indoor unit 53a.
- the remaining gas refrigerant that has flowed into the flow dividing controller 52 passes through the gas-liquid separator 11, the electromagnetic valve 12b, and the gas pipe 204b, and flows into the indoor unit 53b.
- the flow rate of the refrigerant flowing in the indoor heat exchanger 22 is adjusted by adjusting the opening of the indoor expansion device 23.
- the high-pressure gas refrigerant is condensed by heat exchange while passing through the indoor heat exchanger 22, and becomes a liquid refrigerant, and passes through the indoor expansion device 23.
- the indoor air is heated by heat exchange to heat the air-conditioning target space (indoor).
- the refrigerant that has passed through the indoor expansion device 23 becomes, for example, an intermediate-pressure liquid refrigerant or a gas-liquid two-phase refrigerant, passes through the liquid pipe 203, flows into the inter-refrigerant heat exchanger 17, and further passes through the expansion device 15.
- the refrigerant that has been reduced in pressure after passing through the expansion device 15 flows into the low-pressure pipe 201, is distributed to the outdoor unit 51 side and the outdoor unit 151 side at the refrigerant branch point 19, and flows into the outdoor unit 51 and the outdoor unit 151, respectively.
- the refrigerant flowing into the outdoor unit 51 passes through the check valve 5b of the outdoor unit 51 and flows into the heat source side heat exchanger 2. Note that the refrigerant does not flow to the check valve 5a and check valve 5d side due to the pressure of the refrigerant.
- the refrigerant evaporates by heat exchange with air while passing through the heat source side heat exchanger 2, and becomes a gas refrigerant. Then, the refrigerant passes through the four-way valve 3 and the accumulator 4 and returns to the compressor 1 to be discharged again. This is the refrigerant circulation path during the all-heating operation.
- the refrigerant that has flowed into the outdoor unit 151 passes through the check valve 105b of the outdoor unit 151 and flows into the heat source side heat exchanger 102. Note that the refrigerant does not flow to the check valve 105a and the check valve 105d side due to the pressure of the refrigerant. The refrigerant evaporates by heat exchange with air while passing through the heat source side heat exchanger 102 and becomes a gas refrigerant. Then, the refrigerant passes through the four-way valve 103 and the accumulator 104 and returns to the compressor 101 to be discharged again. This is the refrigerant circulation path during the all-heating operation.
- the air conditioner 500 having a plurality of outdoor units such as the air conditioner 500 according to the present embodiment, has a refrigerant bias between the outdoor units due to various factors, particularly during heating operation or heating main operation. There is. There is a correlation between the refrigerant bias and the degree of superheat (compressor suction superheat) at the outlet of the heat source side heat exchanger and the discharge superheat degree of the compressor. That is, when the amount of refrigerant in the outdoor unit decreases, the degree of superheat at the outlet of the heat source side heat exchanger and the degree of discharge superheat of the compressor increase. In other words, when the amount of refrigerant in the outdoor unit increases, the degree of superheat at the outlet of the heat source side heat exchanger and the degree of discharge superheat of the compressor decrease.
- FIG. 3 is a flowchart relating to the control operation of the control unit during the heating operation of the air-conditioning apparatus according to the embodiment of the present invention.
- the liquid equalization control during the heating operation of the air-conditioning apparatus according to the embodiment of the present invention will be described based on the steps in FIG.
- Step S30a As shown in the following equation (1), the heat exchanger outlet superheat degree calculation means 38 calculates the saturation temperature Te1 from the suction pressure (low pressure) detected by the low pressure detection means 32, and detects the heat exchanger outlet temperature. By subtracting the saturation temperature Te1 from the temperature Thex1 detected by the means 35, the heat exchanger outlet superheat degree HEXSH1 is obtained.
- HEXSH1 Thex1-Te1 (1)
- the heat exchanger outlet superheat degree calculating means 138 calculates the saturation temperature Te2 from the discharge pressure (low pressure) detected by the low pressure detecting means 132, and the heat exchanger outlet By subtracting this saturation temperature Te2 from the temperature Thex2 detected by the temperature detection means 135, the heat exchanger outlet superheat degree HEXSH2 is obtained.
- HEXSH2 Thex2-Te2 (2)
- the control unit 20 proceeds to (Step S30b).
- the heat exchanger outlet superheat degree calculation means 38 and 138 are used to determine the heat exchanger outlet superheat degrees HEXSH1 and HEXSH2.
- the present invention is not limited to this, and the controller 20 obtains the heat exchanger outlet superheat degrees. May be.
- the heat exchanger outlet superheat degrees HEXSH1 and HEXSH2 correspond to the “first superheat degree” in the present invention.
- the compressor discharge superheat degree calculation means 137 calculates the saturation temperature Tc2 from the discharge pressure (high pressure) detected by the high pressure detection means 131, and detects the compressor discharge temperature.
- the discharge superheat degree TdSH2 of the compressor 101 is obtained by subtracting the saturation temperature Tc2 from the discharge temperature Td2 detected by the means 134.
- TdSH2 Td2-Tc2 (4)
- the control unit 20 proceeds to (Step S31).
- the compressor discharge superheat degrees TdSH1 and TdSH2 are obtained by the compressor discharge superheat degree calculation means 37 and 137, but the present invention is not limited to this, and is obtained by the control unit 20. Also good.
- the discharge superheat degrees TdSH1 and TdSH2 of the compressor correspond to the “second superheat degree” in the present invention.
- Step S31 The control unit 20 determines whether or not the heat exchanger outlet superheat degree HEXSH1 and the heat exchanger outlet superheat degree HEXSH2 are both greater than a preset reference value A.
- the control unit 20 proceeds to (Step S32). In this case, the process proceeds to (Step S33).
- Step S32 The control unit 20 determines whether or not the discharge superheat degree TdSH1 of the compressor 1 and the discharge superheat degree TdSH2 of the compressor 101 are both larger than a preset reference value B.
- the control unit 20 performs normal operation of the blower 6 and the blower 106. While performing, the process proceeds to (Step S31). In other cases, the process proceeds to (Step S33) to perform liquid leveling control.
- Step S33 The control unit 20 acquires the temperature of the outside air sucked by the outdoor unit 51 and the outdoor unit 151 from the outside air temperature detection unit 36 and the outside air temperature detection unit 136, and determines whether or not the temperature of the outside air is higher than the reference temperature C. If the outside air temperature is higher than the reference temperature C, the control unit 20 proceeds to (Step S34), and otherwise, proceeds to (Step S36).
- Step S34 The control unit 20 acquires information on the operating capacity of the indoor unit 53 from the indoor unit operating capacity calculating unit 41 and the indoor unit operating capacity calculating unit 141, and determines whether or not the operating capacity of the indoor unit 53 is smaller than the reference capacity D. To do. When the operation capacity of the indoor unit 53 is smaller than the reference capacity D, the control unit 20 proceeds to (Step S35), and otherwise, proceeds to (Step S36).
- Step S35 The control unit 20 sets the maximum value of the operation output of the blower 6 and the blower 106 to E, which is the same value as the output of the blower during normal operation. Thereafter, the control unit 20 proceeds to (Step S39).
- the time of normal operation means the time of heating operation when liquid leveling control is not performed, and the maximum output of the blower in that case is the maximum value E of the operation output of the blower.
- Step S36 The control unit 20 determines the blower operation output doubling coefficient H according to the temperature of the outside air and the operation capacity of the indoor unit 53. However, the blower operation output doubling coefficient H is set to a value larger than 1. Thereafter, the control unit 20 proceeds to (Step S37).
- Step S37 The control unit 20 determines that the heating load is high and increases the operation output from the normal operation of the blower. Therefore, the controller 20 multiplies E, which is the operation output of the blower during the normal operation, by a fan operation output doubling factor H, The value is determined as the blower air volume maximum value F. Thereafter, the control unit 20 proceeds to (Step S38).
- Step S38 The control unit 20 sets the operation output that exceeds the operation output of the blower during normal operation, with the maximum value of the operation output of the blower as the blower airflow maximum value F. Thereafter, the control unit 20 proceeds to (Step S39).
- Step S39 The control unit 20 determines whether or not TdSH1> TdSH2. If TdSH1> TdSH2, the control unit 20 proceeds to (Step S40), and otherwise proceeds to (Step S41).
- Step S40 The control unit 20 decreases the operation output of the blower 6 and increases the operation output of the blower 106. Thereafter, the control unit 20 proceeds to (Step S31).
- Step S41 The control unit 20 increases the operation output of the blower 6 and decreases the operation output of the blower 106. Thereafter, the control unit 20 proceeds to (Step S31).
- the case where the liquid leveling means by the blower has a small heat exchanger capacity on the outdoor unit 51 side with respect to the refrigerant circulation amount and the liquid refrigerant is unevenly distributed on the outdoor unit 51 side will be described as an example.
- the heat source side heat from the refrigerant branch point 19 with respect to the refrigerant circulation amount of the compressor 1 and the compressor 101 The degree of superheat to the outlet of the exchanger 2 is made equal to the degree of superheat from the refrigerant branch point 19 to the outlet of the heat source side heat exchanger 102.
- what is necessary is just to make discharge superheat degree of the compressor 1 and the compressor 101 more than a reference value or equivalent.
- TdSH1> TdSH2 is determined, and the heat exchanger outlet superheat degree HEXSH1 of the heat source side heat exchanger 2 and the heat exchanger outlet superheat degree HEXSH2 of the heat source side heat exchanger 102 are the reference values.
- each superheat degree is made to become a reference value. For this purpose, at least the operating output of the blower 6 is increased and the evaporator heat exchange capacity on the outdoor unit 51 side is increased, thereby increasing the degree of superheat at the outlet of the heat source side heat exchanger 2, that is, the degree of dryness. Increase the degree of discharge superheat.
- the outlet superheat degree of the heat source side heat exchanger 102 that is, the dryness is lowered, and the compressor 101 Reduce discharge superheat.
- the superheat degree of the heat source side heat exchanger 2 that is, the dry degree
- the superheat degree of the outlet of the heat source side heat exchanger 102 that is, the dry degree
- the liquid refrigerant is unevenly distributed on the outdoor unit 51 side. That is solved. That is, by increasing the operation output of the blower 6 or decreasing the operation output of the blower 106, the value of TdSH1 and the value of TdSH2 can be brought close to each other, the refrigerant flow rate flowing to the outdoor unit 51 side, and the outdoor unit 151 side The flowing refrigerant flow rate can be adjusted.
- liquid leveling control for selecting the maximum output of the blower of the outdoor unit is performed by determining the air conditioning load according to the outdoor temperature and the indoor unit operating capacity. As a result, it is possible to ensure the required heating capacity and perform liquid leveling control to prevent an increase in the noise of the blower of the outdoor unit when the air conditioning load is small.
- the refrigerant employed in the refrigeration cycle apparatus is not particularly limited.
- carbon dioxide a natural refrigerant such as hydrocarbon or helium
- a refrigerant such as R410A, R32, R407C, R404A, HFO1234yf, or the like.
- R410A, R32, R407C, R404A, HFO1234yf or the like.
- an air conditioner including a plurality of outdoor units equipped with a compressor, a heat source side heat exchanger, and a blower, and an indoor unit equipped with an indoor side heat exchanger.
- An unbalance in the amount of refrigerant in the plurality of outdoor units from the first superheat degree of the refrigerant flowing out from the heat source side heat exchanger and the second superheat degree of the refrigerant discharged from the compressor A control unit that executes liquid leveling control by controlling the operation output of the blower when the air temperature is generated, the control unit has an outdoor temperature greater than a predetermined value, and the indoor unit When the operating capacity is less than a predetermined value, the maximum value of the operating output of the blower is maintained, and when the outdoor temperature is lower than a predetermined value, or when the outdoor temperature is higher than a predetermined value, the indoor unit When the operating capacity is equal to or greater than a predetermined value, the blower The maximum value of the driving output so as to increase.
- adjusting the output of the blower in the outdoor unit and adjusting the output of the compressor frequency, the state of the refrigerant flowing into the heat source side heat exchanger (refrigerant dryness) and the flow rate that is, the outdoor unit It is possible to perform liquid leveling control of each indoor unit while controlling both of the flow rate of the circulating refrigerant) and preventing a decrease in the refrigerant circulation rate.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Signal Processing (AREA)
- Fluid Mechanics (AREA)
- Fuzzy Systems (AREA)
- Mathematical Physics (AREA)
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
[空気調和装置の冷媒回路の説明]
図1は、本発明の実施の形態に係る空気調和装置の概略冷媒回路図である。図1に基づいて、空気調和装置500の冷媒回路の構成について説明する。空気調和装置500は、冷媒を循環させる冷凍サイクル(ヒートポンプサイクル)を利用して、冷房運転及び暖房運転を行うものである。図1に示されるように、空気調和装置500は、熱源側ユニットとして室外機51及び室外機151を備え、負荷側ユニットとして室内機53a、室内機53bを備えている。そして、室外機51及び室外機151が、低圧管201及び高圧管202によって分流コントローラ52に接続され、さらに分流コントローラ52から室内機53a及び室内機53bに並列接続され、冷凍サイクル回路が構成されている。また、空気調和装置500は、後述する制御部20を備えている。なお、図1に示す空気調和装置500はあくまでも一例であり、室外機を3つ以上備えてもよいし、室内機を1つ又は3つ以上にしてもよい。
次に全暖房運転における各機器の動作及び冷媒の流れについて説明する。ここでは、すべての室内機53が停止することなく暖房を行っている場合について説明する。図2は本発明の実施の形態に係る空気調和装置の暖房運転時の冷媒回路図である。全暖房運転時の冷媒の流れは図2に実線矢印で示している。図2に示されるように、室外機51において、圧縮機1は、吸入した冷媒を圧縮し、高圧のガス冷媒を吐出する。圧縮機1が吐出した冷媒は、四方弁3、逆止弁5cを流れ(逆止弁5a、逆止弁5d側には流れない)、さらに冷媒合流点18を経由し、高圧管202を通って分流コントローラ52に流入する。
次に均液制御について説明する。本実施の形態に係る空気調和装置500のように複数の室外機を備えた空気調和装置500は、特に暖房運転時又は暖房主体運転時に種々の要因によって各室外機間に冷媒の偏りが生じる場合がある。そして、この冷媒の偏りと熱源側熱交換器の出口における過熱度(圧縮機の吸入過熱度)及び圧縮機の吐出過熱度との間には、相関関係がある。つまり、室外機内の冷媒量が少なくなると、熱源側熱交換器の出口における過熱度及び圧縮機の吐出過熱度が大きくなる。換言すると、室外機内の冷媒量が多くなると、熱源側熱交換器の出口における過熱度及び圧縮機の吐出過熱度が小さくなる。
次式(1)に示すように、熱交換器出口過熱度演算手段38は、低圧圧力検知手段32で検知された吸入圧力(低圧圧力)から飽和温度Te1を計算し、熱交換器出口温度検知手段35によって検知される温度Thex1からこの飽和温度Te1を減算することにより、熱交換器出口過熱度HEXSH1を求める。
HEXSH1=Thex1-Te1…(1)
HEXSH2=Thex2-Te2…(2)
その後、制御部20は、(ステップS30b)へ移行する。
なお、本実施の形態において熱交換器出口過熱度演算手段38、138により熱交換器出口過熱度HEXSH1、HEXSH2を求める例を示したが、本発明はこれに限定されず、制御部20により求めてもよい。また、熱交換器出口過熱度HEXSH1、HEXSH2は、本発明における「第一の過熱度」に相当する。
次式(3)に示すように、圧縮機吐出過熱度演算手段37は、高圧圧力検知手段31で検知された吐出圧力(高圧圧力)から飽和温度Tc1を計算し、圧縮機吐出温度検知手段34によって検知される吐出温度Td1から、この飽和温度Tc1を減算することにより、圧縮機1の吐出過熱度TdSH1を求める。
TdSH1=Td1-Tc1…(3)
TdSH2=Td2-Tc2…(4)
その後、制御部20は、(ステップS31)へ移行する。
なお、本実施の形態において圧縮機吐出過熱度演算手段37、137により圧縮機の吐出過熱度TdSH1、TdSH2を求める例を示したが、本発明はこれに限定されず、制御部20により求めてもよい。また、圧縮機の吐出過熱度TdSH1、TdSH2は、本発明における「第二の過熱度」に相当する。
制御部20は、熱交換器出口過熱度HEXSH1と、熱交換器出口過熱度HEXSH2とが、共に予め設定してある基準値Aよりも大きいかどうかを判断する。制御部20は、熱交換器出口過熱度HEXSH1と、熱交換器出口過熱度HEXSH2とが、共に予め設定してある基準値Aよりも大きい場合は、(ステップS32)へ移行し、それ以外の場合は、(ステップS33)へ移行する。
制御部20は、圧縮機1の吐出過熱度TdSH1と、圧縮機101の吐出過熱度TdSH2とが、共に予め設定してある基準値Bよりも大きいかどうかを判断する。制御部20は、圧縮機1の吐出過熱度TdSH1と、圧縮機101の吐出過熱度TdSH2とが、共に予め設定してある基準値Bよりも大きい場合は、送風機6及び送風機106の通常運転を行いながら(ステップS31)へ移行し、それ以外の場合は、(ステップS33)へ移行して均液制御を行う。
制御部20は、外気温度検知手段36及び外気温度検知手段136から、室外機51及び室外機151が吸い込む外気の温度を取得し、外気の温度が基準温度Cより大きいか否かを判断する。外気の温度が基準温度Cより大きい場合は、制御部20は、(ステップS34)へ移行し、それ以外の場合は、(ステップS36)へ移行する。
制御部20は、室内機運転容量演算手段41及び室内機運転容量演算手段141から室内機53の運転容量の情報を取得し、室内機53の運転容量が基準容量Dより小さいか否かを判断する。室内機53の運転容量が基準容量Dより小さい場合は、制御部20は、(ステップS35)へ移行し、それ以外の場合は、(ステップS36)へ移行する。
制御部20は、送風機6及び送風機106の運転出力の最大値を、通常運転時の送風機の出力と同じ値であるEに設定する。その後、制御部20は、(ステップS39)へ移行する。なお、通常運転時とは、均液制御を行わない場合の暖房運転時のことを意味し、その場合の送風機の最大出力を送風機の運転出力の最大値Eとする。
制御部20は、外気の温度及び室内機53の運転容量に応じて送風機運転出力倍増係数Hを決定する。ただし、送風機運転出力倍増係数Hは1より大きい値とする。その後、制御部20は、(ステップS37)へ移行する。
制御部20は、暖房負荷が高いと判断し、送風機の通常運転時より運転出力を増加させるため、通常運転時の送風機の運転出力であるEに、送風機運転出力倍増係数Hを乗じて、その値を送風機風量最大値Fとして決定する。その後、制御部20は、(ステップS38)へ移行する。
制御部20は、送風機の運転出力の最大値を送風機風量最大値Fとして、通常運転時の送風機の運転出力を超えた運転出力を設定する。その後、制御部20は、(ステップS39)へ移行する。
制御部20は、TdSH1>TdSH2であるか否かを判断する。TdSH1>TdSH2の場合は、制御部20は、(ステップS40)へ移行し、それ以外の場合は、(ステップS41)へ移行する。
制御部20は、送風機6の運転出力を低下させると共に、送風機106の運転出力を増加させる。その後、制御部20は、(ステップS31)へ移行する。
制御部20は、送風機6の運転出力を増加させると共に、送風機106の運転出力を低下させる。その後、制御部20は、(ステップS31)へ移行する。
Claims (3)
- 圧縮機、熱源側熱交換器、及び送風機を搭載した複数の室外機と、室内側熱交換器を搭載した室内機と、を備えた空気調和装置であって、
暖房運転時又は暖房主体運転時において、前記熱源側熱交換器から流出する冷媒の第一の過熱度と、前記圧縮機から吐出する冷媒の第二の過熱度とから、前記複数の室外機において冷媒量の不均衡が発生していると判断したとき、前記冷媒量が多い方の室外機の送風機の運転出力を増加させ、前記冷媒量の少ない方の室外機の送風機の運転出力を低下させることで均液制御を実行する制御部を備え、
前記制御部は、
室外温度が基準温度より大きく、かつ、前記室内機の運転容量が基準容量未満である場合には、前記送風機を通常運転時の運転出力の最大値の範囲内で均液制御を実行し、
室外温度が基準温度以下の場合、又は、室外温度が基準温度以上より大きく前記室内機の運転容量が基準容量以上である場合には、前記送風機を通常運転時の運転出力の最大値より増加させて均液制御を実行する
空気調和装置。 - 前記制御部は、
前記圧縮機の吸入側の冷媒の低圧圧力、及び、前記熱源側熱交換器の出口側の冷媒の温度により、前記第一の過熱度を演算し、
前記圧縮機の吐出側の冷媒の高圧圧力、及び、前記圧縮機の吐出側の冷媒の温度により、前記第二の過熱度を演算する
請求項1に記載の空気調和装置。 - 前記制御部は、前記第一の過熱度のそれぞれ、及び、前記第二の過熱度のそれぞれを基準値に収束するように前記送風機を運転制御する
請求項2に記載の空気調和装置。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2015/067868 WO2016207947A1 (ja) | 2015-06-22 | 2015-06-22 | 空気調和装置 |
JP2017524289A JP6370489B2 (ja) | 2015-06-22 | 2015-06-22 | 空気調和装置 |
GB1800124.8A GB2555063B (en) | 2015-06-22 | 2015-06-22 | Air-conditioning apparatus |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2015/067868 WO2016207947A1 (ja) | 2015-06-22 | 2015-06-22 | 空気調和装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016207947A1 true WO2016207947A1 (ja) | 2016-12-29 |
Family
ID=57585188
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2015/067868 WO2016207947A1 (ja) | 2015-06-22 | 2015-06-22 | 空気調和装置 |
Country Status (3)
Country | Link |
---|---|
JP (1) | JP6370489B2 (ja) |
GB (1) | GB2555063B (ja) |
WO (1) | WO2016207947A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108361834A (zh) * | 2018-02-06 | 2018-08-03 | 青岛海尔空调器有限总公司 | 一拖多空调的控制方法、装置及空调器 |
CN109612018A (zh) * | 2018-11-26 | 2019-04-12 | 宁波奥克斯电气股份有限公司 | 一种调节空调器排气过热度的控制方法及空调器 |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP7258129B2 (ja) * | 2019-05-21 | 2023-04-14 | 三菱電機株式会社 | 空気調和装置 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11142010A (ja) * | 1997-11-12 | 1999-05-28 | Mitsubishi Electric Corp | 冷凍空気調和装置 |
JP2008249259A (ja) * | 2007-03-30 | 2008-10-16 | Mitsubishi Electric Corp | 冷凍空気調和装置 |
JP2010261715A (ja) * | 2010-08-27 | 2010-11-18 | Mitsubishi Electric Corp | 空気調和装置 |
JP2011085390A (ja) * | 2005-10-25 | 2011-04-28 | Mitsubishi Electric Corp | 空気調和装置 |
JP2011208928A (ja) * | 2010-03-31 | 2011-10-20 | Hitachi Appliances Inc | 空気調和機 |
WO2014054154A1 (ja) * | 2012-10-04 | 2014-04-10 | 三菱電機株式会社 | 空気調和装置 |
-
2015
- 2015-06-22 WO PCT/JP2015/067868 patent/WO2016207947A1/ja active Application Filing
- 2015-06-22 JP JP2017524289A patent/JP6370489B2/ja not_active Expired - Fee Related
- 2015-06-22 GB GB1800124.8A patent/GB2555063B/en not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11142010A (ja) * | 1997-11-12 | 1999-05-28 | Mitsubishi Electric Corp | 冷凍空気調和装置 |
JP2011085390A (ja) * | 2005-10-25 | 2011-04-28 | Mitsubishi Electric Corp | 空気調和装置 |
JP2008249259A (ja) * | 2007-03-30 | 2008-10-16 | Mitsubishi Electric Corp | 冷凍空気調和装置 |
JP2011208928A (ja) * | 2010-03-31 | 2011-10-20 | Hitachi Appliances Inc | 空気調和機 |
JP2010261715A (ja) * | 2010-08-27 | 2010-11-18 | Mitsubishi Electric Corp | 空気調和装置 |
WO2014054154A1 (ja) * | 2012-10-04 | 2014-04-10 | 三菱電機株式会社 | 空気調和装置 |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108361834A (zh) * | 2018-02-06 | 2018-08-03 | 青岛海尔空调器有限总公司 | 一拖多空调的控制方法、装置及空调器 |
CN109612018A (zh) * | 2018-11-26 | 2019-04-12 | 宁波奥克斯电气股份有限公司 | 一种调节空调器排气过热度的控制方法及空调器 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2016207947A1 (ja) | 2018-01-25 |
GB2555063A (en) | 2018-04-18 |
GB2555063B (en) | 2020-08-19 |
GB201800124D0 (en) | 2018-02-21 |
JP6370489B2 (ja) | 2018-08-08 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CN108027179B (zh) | 空气调节机 | |
EP3467406A1 (en) | Air conditioner | |
JP6479162B2 (ja) | 空気調和装置 | |
JP6067025B2 (ja) | 空気調和装置 | |
WO2013145006A1 (ja) | 空気調和装置 | |
JP6223469B2 (ja) | 空気調和装置 | |
US10415846B2 (en) | Air-conditioning apparatus | |
CN109791003B (zh) | 空调装置 | |
CN109791007B (zh) | 空调装置 | |
JP6644131B2 (ja) | 空気調和装置 | |
WO1998009118A1 (fr) | Conditionneur d'air | |
WO2017138108A1 (ja) | 空気調和装置 | |
US20190249912A1 (en) | Air conditioner | |
JPWO2019053876A1 (ja) | 空気調和装置 | |
JPWO2019058506A1 (ja) | 空気調和装置 | |
JP6370489B2 (ja) | 空気調和装置 | |
JP6246394B2 (ja) | 空気調和装置 | |
WO2016170575A1 (ja) | 冷凍サイクル装置 | |
JP6949126B2 (ja) | 空気調和装置 | |
JP2012137241A (ja) | 空気調和装置 | |
GB2555258A (en) | Air conditioning device | |
WO2014054154A1 (ja) | 空気調和装置 | |
JP2011058749A (ja) | 空気調和装置 | |
JP6198945B2 (ja) | 空気調和装置 | |
JP6704520B2 (ja) | 中継機および空気調和装置 |
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: 15896270 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2017524289 Country of ref document: JP Kind code of ref document: A |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: 201800124 Country of ref document: GB Kind code of ref document: A Free format text: PCT FILING DATE = 20150622 |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 15896270 Country of ref document: EP Kind code of ref document: A1 |