WO2016117126A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
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- WO2016117126A1 WO2016117126A1 PCT/JP2015/051913 JP2015051913W WO2016117126A1 WO 2016117126 A1 WO2016117126 A1 WO 2016117126A1 JP 2015051913 W JP2015051913 W JP 2015051913W WO 2016117126 A1 WO2016117126 A1 WO 2016117126A1
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- refrigerant
- compressor
- superheat degree
- heat source
- control
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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
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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
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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
- F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
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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
- F24F11/72—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
- F24F11/76—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 by means responsive to temperature, e.g. bimetal springs
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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
- F24F11/81—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the air supply to heat-exchangers or bypass channels
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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
- F24F11/70—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
- F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B45/00—Arrangements for charging or discharging refrigerant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
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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
- F24F2110/00—Control inputs relating to air properties
- F24F2110/10—Temperature
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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
- F24F2140/00—Control inputs relating to system states
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
- F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/06—Several compression cycles arranged in parallel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
Definitions
- the present invention relates to an air conditioner having a refrigeration cycle configured by combining two or more heat source machines.
- the superheat degree of the refrigerant flowing out from the heat source side heat exchanger and the discharge from the compressor are controlled by controlling the operation output of the blower that blows air to the heat source side heat exchanger provided in the heat source device.
- Liquid leveling control is executed by converging the degree of superheat of the refrigerant to a predetermined value set in advance (see Patent Document 1).
- liquid leveling is achieved by controlling the operation output of the blower for supplying air to the heat source side heat exchanger of the heat source machine, and the air volume of the blower is reduced or increased. There is a need to. When the air volume is reduced, the compressor suction pressure is reduced and the refrigerant circulation rate is reduced. For this reason, there is a problem that the air conditioning capability may be impaired during the liquid leveling control depending on the degree of decrease in the air volume.
- the present invention has been made to solve the above-described problems, and an object of the present invention is to obtain an air conditioner capable of maintaining air conditioning capability during liquid leveling control.
- the air conditioner according to the present invention includes a plurality of heat source units each including a compressor, a heat source side heat exchanger, an accumulator, and a blower that supplies air to the heat source side heat exchanger, and a liquid refrigerant amount between the plurality of accumulators.
- Imbalance detection means for detecting the presence or absence of imbalance
- heat exchange amount calculation means for calculating the total heat exchange amount of the plurality of heat source side heat exchangers
- circulation amount calculation for calculating the total refrigerant circulation amount of the plurality of heat source units
- control means for performing liquid leveling control to correct the imbalance when the imbalance detection means detects that there is an imbalance, and the control means performs output control of the blower to perform liquid leveling control.
- the second leveling liquid control unit includes liquid leveling control using frequency control of the compressor.
- the total refrigerant circulation rate was set in advance The amount of increase / decrease in the frequency of the compressor is determined so as not to fall below the fixed amount.
- the control means When the calculated value of the heat exchange amount calculating means is within a predetermined allowable range, the control means When the calculation value of the heat exchange amount calculation means is outside the allowable range, the second liquid leveling control means is selected to perform liquid leveling control.
- an air conditioner capable of maintaining the air conditioning capability during the liquid leveling control.
- FIG. 1 is a refrigerant circuit diagram illustrating a refrigerant circuit of an air-conditioning apparatus according to Embodiment 1 of the present invention. Based on this FIG. 1, the circuit structure 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 shown in FIG. 1 includes a heat source unit (heat source unit 51 and heat source unit 151) that is a heat source side unit, and redundant functional components are mounted on each heat source unit.
- the air conditioner 500 illustrated in FIG. 1 is merely an example, and may include three or more heat source devices, or may include a plurality of usage-side units that are load-side units.
- the air conditioner 500 includes two heat source machines (a heat source machine 51 and a heat source machine 151) and two usage side machines (a usage side machine 53a and a usage side machine 53b).
- the heat source device 51 and the heat source device 151 are connected in parallel to the two usage side units (the usage side unit 53a and the usage side unit 53b) by the low-pressure pipe 201 and the high-pressure pipe 202, thereby forming a refrigeration cycle circuit.
- the heat source device 51 includes the compressor 1 (101), the heat source side heat exchanger 2 (102), the four-way valve 3 (103), the accumulator 4 (104), the check valves 5a, 5b, 5c, 5d (105a). , 105b, 105c, 105d).
- the heat source device 51 (151) further includes a discharge pressure detection means 31 (131), a suction pressure detection means 32 (132), a discharge temperature detection means 34 (134), a heat exchanger outlet temperature detection means 35 (135), and an outside air temperature.
- the detection means 36 (136) is provided.
- a four-way valve 3 (103) is connected to the discharge side of the compressor 1 (101).
- the four-way valve 3 (103) is a flow path or a use side machine (use side machine 53a, use side machine 53b) that flows through the flow path of the refrigerant discharged from the compressor 1 (101) to the heat source side heat exchanger 2 (102). ) Is switched to the flow path.
- the four-way valve 3 (103) is also connected to the accumulator 4 (104), and the refrigerant flowing from the heat source side heat exchanger 2 (102) or the use side machine (use side machine 53a, use side machine 53b) is supplied. The data is sent to the accumulator 4 (104).
- the air conditioner of the first embodiment can perform a cooling operation and a heating operation by switching the four-way valve 3 (103).
- the four-way valve 3 (103) corresponds to the flow path switching device of the present invention.
- the flow path switching device is not limited to a four-way switching valve, and may be configured by combining, for example, a two-way valve or the like.
- the air conditioner 500 of the first embodiment further includes a shunt controller 52 between the heat source unit 51 (151) and the use side unit 53 (use side unit 53a, use side unit 53b) in order to control the flow of the refrigerant. These devices are connected by various refrigerant pipes.
- the plurality of usage side machines 53a and 53b are connected in parallel to each other. For example, in the usage side machine 53a, the usage side machine 53b, and the like, there is a case where the subscripts “a” and “b” are omitted in the following description when there is no need to distinguish or specify.
- the low-pressure pipe 201 and the high-pressure pipe 202 are connected between the heat source device 51 (151) and the shunt controller 52.
- the low pressure pipe 201 connected to the heat source machine 51 and the diversion controller 52 and the low pressure pipe 201 connected to the heat source machine 151 and the diversion controller 52 are connected by the liquid side merging section 18 and the gas side merging section 19. .
- a high-pressure refrigerant flows from the heat source device 51 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 heat source unit 51 (151).
- the level of the pressure is not determined based on the relationship with the reference pressure (numerical value), but the pressurization of the compressor 1 (101) and the opening / closing of each throttle device (flow restriction device). In accordance with the control of the (opening) state and the like, it is expressed based on relative height (including the middle) in the refrigerant circuit.
- the diversion controller 52 and the use side machine 53a are connected by the liquid pipe 203a and the gas pipe 204a.
- the diversion controller 52 and the use side unit 53b are connected by a liquid pipe 203b and a gas pipe 204b.
- the heat source device 51 151
- the shunt controller The refrigerant circulates between 52 and the use side machine 53, and a refrigerant circuit is configured.
- the heat source side heat exchanger 2 (102) has a heat transfer tube through which the refrigerant passes and fins for increasing the heat transfer area between the refrigerant flowing through the heat transfer tube and the outside air, and the refrigerant and air (outside air) Heat exchange.
- the heat source side heat exchanger 2 (102) functions as an evaporator, and evaporates and evaporates, for example, a refrigerant.
- the heat source side heat exchanger 2 (102) functions as a condenser, for example, condenses and liquefies the refrigerant.
- the gas is not completely gasified or liquefied but is adjusted to be condensed to a state of two-phase mixing of gas and liquid (gas-liquid two-phase state). Done.
- Check valves 5a, 5b, 5c, and 5d (105a, 105b, 105c, and 105d) prevent the refrigerant from flowing backward, regulate the flow of the refrigerant, and make the circulation path of the refrigerant unidirectional regardless of the operation mode. It is.
- the check valve 5a (105a) is located on the pipe between the four-way valve 3 (103) and the low-pressure pipe 201, and allows the refrigerant flow from the low-pressure pipe 201 to the four-way valve 3 (103).
- the check valve 5b (105b) is located on the pipe between the heat source side heat exchanger 2 (102) and the low pressure pipe 201, and the refrigerant flows from the low pressure pipe 201 to the heat source side heat exchanger 2 (102).
- the check valve 5c (105c) is located on the pipe between the four-way valve 3 (103) and the high-pressure pipe 202, and allows the refrigerant flow from the four-way valve 3 (103) to the high-pressure pipe 202.
- the check valve 5d (105d) is located on the pipe between the heat source side heat exchanger 2 (102) and the high pressure pipe 202, and the refrigerant flows from the heat source side heat exchanger 2 (102) to the high pressure pipe 202. Allow flow.
- the discharge pressure detection means 31 (131) and the discharge temperature detection means 34 (134) are attached to the piping on the discharge side of the compressor 1 (101).
- the discharge pressure detection means 31 (131) detects the refrigerant pressure on the compressor discharge side.
- the discharge temperature detection means 34 (134) detects the temperature of the refrigerant on the compressor discharge side.
- suction pressure detection means 32 (132) and heat exchanger outlet temperature detection means 35 (135) are attached on the pipe on the suction side of the compressor 1 (101).
- the suction pressure detection means 32 (132) detects the pressure of the refrigerant on the outlet side of the heat source side heat exchanger 2 (102) during the heating operation.
- the heat exchanger outlet temperature detection means 35 (135) detects the temperature on the outlet side of the heat source side heat exchanger 2 (102) during the heating operation. In other words, the heat exchanger outlet temperature detection means 35 (135) detects the temperature of the refrigerant sucked into the compressor 1 (101).
- the air conditioner 500 further includes outside air temperature detecting means 36 (136) for detecting the ambient temperature of the heat source device 51 (151).
- the discharge temperature detecting means 34 (134), the heat exchanger outlet temperature detecting means 35 (135), and the outside air temperature detecting means 36 (136) are constituted by temperature sensors such as a thermistor. Further, the discharge pressure detection means 31 (131) and the suction pressure detection means 32 (132) are constituted by pressure sensors or the like.
- the heat source unit 51 further includes a discharge superheat degree calculating means 37 (137), a heat exchanger outlet superheat degree calculating means 38 (138), a heat exchange amount calculating means 39 (139), and a circulation amount calculating means 40. (140).
- Each of these calculation means can be configured by hardware such as a circuit device that realizes the function, or is configured by using a calculation device such as a microcomputer or a CPU and software executed on the calculation device. You can also The discharge superheat degree calculating means 37, the discharge superheat degree calculating means 137, the heat exchanger outlet superheat degree calculating means 38, and the heat exchanger outlet superheat degree calculating means 138 are used to reduce the amount of liquid refrigerant between the accumulators 4 and 104.
- the imbalance detection means of the present invention for detecting the presence or absence is configured.
- the discharge superheat degree calculation means 37 (137) compresses using the discharge pressure detected by the discharge pressure detection means 31 (131) and the discharge temperature Td1 (Td2) detected by the discharge temperature detection means 34 (134).
- the discharge superheat degree TdSH1 (TdSH2) of the machine 1 (101) is calculated by the expressions (1) and (2).
- TdSH1 Td1-Tc1 (1)
- TdSH2 Td2-Tc2 (2) here, Tc1 [° C.]: Saturation temperature obtained by converting the discharge pressure detected by the discharge pressure detecting means 31 into saturation
- Tc2 Saturation temperature obtained by converting the discharge pressure detected by the discharge pressure detecting means 131 into saturation
- TdSH the compressor discharge superheat degree
- the heat exchanger outlet superheat degree calculation means 38 (138) includes the suction pressure detected by the suction pressure detection means 32 (132) and the temperature Thex1 (Thex2) detected by the heat exchanger outlet temperature detection means 35 (135). Based on the above, the outlet superheat degree HEXSH1 (HEXSH2) of the heat source side heat exchanger 2 (102) is calculated by (3) and Expression (4).
- HEXSH1 Thex1-Te1 (3)
- HEXSH2 Thex2-Te2 (4) here, Thex1 [° C.]: Saturation temperature obtained by converting the suction pressure detected by the suction pressure detecting means 32 into saturation
- HEXSH the heat exchanger outlet superheat degree
- the heat exchange amount calculation means 39 calculates the heat exchange amount AK1 (AK2) of the heat source side heat exchanger 2 (102) by the equations (5) and (6).
- the circulation amount calculation means 40 calculates the refrigerant circulation amount Gr1 (Gr2) of the heat source unit 51 (151) by the equations (7) and (8).
- the air conditioner 500 further includes a control unit 100 that controls the entire air conditioner 500.
- the control means 100 calculates the discharge superheat degree calculation means 37 (137), the heat exchanger outlet superheat degree calculation means 38 (138), the heat exchange amount calculation means 39 (139), and the circulation amount calculation means 40 (140). Get the value.
- the control means 100 controls the four-way valve 3 (103) associated with the switching between the cooling operation and the heating operation, etc., based on the acquired calculated value, to correct the liquid amount imbalance in the accumulator 4 and the accumulator 104, etc. Various controls are performed.
- the control means 100 can be configured by hardware such as a circuit device that realizes the function, or can be configured by using an arithmetic device such as a microcomputer or CPU and software executed on the arithmetic device. it can.
- the discharge superheat degree calculating means 37 (137), the heat exchanger outlet superheat degree calculating means 38 (138), the heat exchange amount calculating means 39 (139), and the circulation amount calculating means 40 (140) are functions of the control means 100. It is good also as one of these.
- control device 20 As a means for performing liquid leveling control, the control device 20 performs output control of the blower 6 (106) to correct the liquid amount imbalance, and performs frequency control of the compressor 1 (101). And a second liquid leveling control means 100b for correcting the liquid volume imbalance. Liquid leveling control using these liquid leveling control means 100a and 100b will be described in detail again.
- the operation modes performed in the air conditioning apparatus 500 of the first embodiment include a cooling operation and a heating operation.
- the cooling operation includes a cooling operation (in this case, the operation when all the air-conditioned users are cooling) and a cooling main operation (a cooling load in the simultaneous cooling and heating operation). Is a big driving).
- the heating operation includes a heating operation (in this case, an operation when all the air-conditioning users are heating) and a heating main operation (a heating load in the simultaneous cooling / heating operation). Is a big driving).
- 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.
- the gas phase part (not shown) from which the gas refrigerant flows out is connected to a branch flow side opening / closing valve 12 (12a, 12b) composed of an electromagnetic valve.
- a liquid phase part (not shown) from which the liquid refrigerant flows is connected to the inter-refrigerant heat exchanger 16.
- the diversion-side opening / closing valve 12 (12a, 12b) and the diversion-side opening / closing valve 13 (13a, 13b) open and close according to the operation mode.
- One end of the diversion-side opening / closing valve 12 (12a, 12b) is connected to the gas-liquid separator 11, and the other end is connected to the gas pipe 204 (204a, 204b).
- one end of the flow dividing side opening / closing valve 13 (13a, 13b) is connected to the gas pipe 204 (204a, 204b), and the other end is connected to the low pressure pipe 201.
- the refrigerant flows from the use side machine 53 side to the low pressure pipe 201 side according to the operation mode by combining the diversion side on / off valve 12 (12a, 12b) and the diversion side on / off valve 13 (13a, 13b) and switching them appropriately.
- the refrigerant may flow from the gas-liquid separator 11 side to the use side unit 53 side.
- the flow of the refrigerant is switched using the flow dividing on-off valve 12 and the flow dividing on-off valve 13, but a three-way valve or the like may be used, for example.
- the expansion device 14 is provided between the inter-refrigerant heat exchanger 16 and the inter-refrigerant heat exchanger 17, the opening degree is controlled according to the operation mode, and the refrigerant flow rate of refrigerant flowing out of the gas-liquid separator 11 and the refrigerant Adjust the pressure.
- the expansion device 15 adjusts the refrigerant flow rate and the refrigerant pressure of the refrigerant flowing out from the inter-refrigerant heat exchanger 17.
- the refrigerant that has passed through the expansion device 15 supercools the refrigerant in the inter-refrigerant heat exchanger 17 and the inter-refrigerant heat exchanger 16, for example, and flows into the low-pressure pipe 201.
- the inter-refrigerant heat exchanger 17 has a high-pressure channel and a low-pressure channel, and performs heat exchange between the refrigerant passing through the high-pressure channel and the refrigerant passing through the low-pressure channel.
- the refrigerant flowing from the expansion device 14 and the refrigerant flowing from the liquid pipes 203a and 203b pass through the high-pressure side flow path.
- the refrigerant in the downstream portion of the expansion device 15 (the refrigerant that has passed through the expansion device 15) passes through the low-pressure side flow path.
- the inter-refrigerant heat exchanger 16 has a high-pressure channel and a low-pressure channel, and performs heat exchange between the refrigerant passing through the high-pressure channel and the refrigerant passing through the low-pressure channel.
- Liquid refrigerant flowing from the gas-liquid separator 11 in the direction of the expansion device 14 passes through the high-pressure side flow path of the inter-refrigerant heat exchanger 16.
- the refrigerant that has passed through the low-pressure channel of the inter-refrigerant heat exchanger 17 passes through the low-pressure channel of the inter-refrigerant heat exchanger 16.
- the use side machine 53 includes a use side heat exchanger 22 (22a, 22b) and a use side expansion device 23 (23a, 23b) connected in series near the use side heat exchanger 22.
- the use side heat exchanger 22 serves as an evaporator during the cooling operation, and serves as a condenser during the heating operation, and performs heat exchange between the air and the refrigerant in the air-conditioning target space.
- a blower for efficiently performing heat exchange between the refrigerant and the air may be provided in the vicinity of each use-side heat exchanger 22.
- the use side expansion device 23 functions as a pressure reducing valve or an expansion valve, and adjusts the pressure of the refrigerant passing through the use side heat exchanger 22.
- the use-side throttle device 23 according to the first embodiment is composed of, for example, an electronic expansion valve that can change the opening degree.
- the opening degree of the use side expansion device 23 is determined based on the degree of superheat on the refrigerant outlet side (here, the gas pipe 204 side) of the use side heat exchanger 22 during the cooling operation.
- the opening degree of the use side expansion device 23 is determined based on the degree of supercooling on the refrigerant outlet side (here, the liquid pipe 203 side) of the use side heat exchanger 22 during the heating operation.
- the air conditioning apparatus 500 operates 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 performed. Since the refrigerant is biased during the heating operation, the refrigerant flow in the heating operation will be described below, and the refrigerant flow in the cooling operation is not related to the gist of the present invention and will be omitted.
- FIG. 2 is a diagram showing the refrigerant flow in the heating only operation in the air-conditioning apparatus according to Embodiment 1 of the present invention.
- the operation of each device and the flow of the refrigerant in the heating only operation will be described with reference to FIG.
- the flow of the refrigerant in the all heating operation is indicated by solid line arrows in FIG.
- the compressor 1 (101) compresses the sucked refrigerant and discharges the high-pressure gas refrigerant.
- the refrigerant discharged from the compressor 1 (101) flows through the four-way valve 3 (103) and the check valve 5c (105c) (the check valve 5a (105a) and the check valve 5d (105d) due to the refrigerant pressure). And flow into the shunt controller 52 through the high-pressure pipe 202.
- the diversion controller 52 opens the diversion side on / off valve 12 (12a, 12b) and closes the diversion side on / off valve 13 (13a, 13b) during the all-heating operation. Further, the expansion device 14 is fully closed. Therefore, the gas refrigerant that has flowed into the flow dividing controller 52 passes through the gas-liquid separator 11, the flow dividing on-off valves 12 (12a, 12b) and the gas pipes 204a, 204b, and flows into the use side machines 53a, 53b.
- the flow rate of the refrigerant flowing in the use side heat exchangers 22a and 22b is adjusted by adjusting the opening of the use side expansion devices 23a and 23b.
- the high-pressure gas refrigerant that has flowed into the use side heat exchangers 22a and 22b condenses into a liquid refrigerant by heat exchange with the indoor air while passing through the use side heat exchangers 22a and 22b. It passes through the devices 23a and 23b. At this time, the indoor air is heated by heat exchange to heat the air-conditioning target space (indoor).
- the refrigerant that has passed through the use-side expansion devices 23a and 23b becomes, for example, an intermediate-pressure liquid refrigerant or a gas-liquid two-phase refrigerant, passes through the liquid pipes 203a and 203b, and flows to the inter-refrigerant heat exchanger 17, and further the expansion device 15 Pass through.
- the refrigerant that has passed through the expansion device 15 and has been depressurized flows from the branch-side bypass pipe 205 to the low-pressure pipe 201 and flows into the heat source unit 51 (151).
- the refrigerant that has flowed into the heat source device 51 (151) passes through the check valve 5b (105b) of the heat source device 51 (151) and flows into the heat source side heat exchanger 2 (102). While passing through the heat source side heat exchanger 2 (102), it evaporates by heat exchange with air and becomes a gas refrigerant. And it returns to the compressor 1 (101) again through the four-way valve 3 (103) and the accumulator 4 (104), and is discharged. This is the refrigerant circulation path during the all-heating operation.
- the refrigerant may be biased between the heat source units due to various factors.
- the refrigerant bias and the suction superheat and discharge superheat of the compressor. That is, when the amount of refrigerant in the heat source device decreases, the suction superheat degree and the discharge superheat degree of the compressor increase. On the other hand, when the amount of refrigerant in the heat source device increases, the suction superheat degree and the discharge superheat degree of the compressor become small.
- the relationship that the discharge superheat degree TdSH1 of the compressor 1 is ideally equal to the discharge superheat degree TdSH2 of the compressor 101 is established.
- the discharge superheat degree TdSH1 of the compressor 1 is determined according to the refrigerant holding amount in the heat source unit 51.
- a difference arises between the discharge superheat degree TdSH2 of the compressor 101. For example, when the refrigerant holding amount in the heat source device 151 is smaller than the refrigerant holding amount in the heat source device 51, TdSH1 ⁇ TdSH2.
- the following liquid leveling control is performed to correct the deviation of the refrigerant between the heat source units.
- the outlet superheat degree of the heat source side heat exchanger 2 (102) also changes following the change in the discharge superheat degree of the compressor 1 (101)
- the first embodiment will be described below.
- control is adopted in which the discharge superheat degree TdSH1 of the compressor 1 and the discharge superheat degree TdSH2 of the compressor 101 are converged to predetermined values.
- the predetermined value may be a value set in advance, or may be a value that varies according to the values of the discharge superheat degree TdSH1 and the discharge superheat degree TdSH2 during operation.
- the value that fluctuates depending on the values of the discharge superheat degree TdSH1 and the discharge superheat degree TdSH2 during operation is a predetermined value that is the discharge superheat degree TdSH1 or the discharge superheat degree TdSH2 itself when it is detected that there is a refrigerant imbalance.
- a value between the discharge superheat degree TdSH1 and the discharge superheat degree TdSH2 may be set as a predetermined value.
- the outlet superheat degrees HEXSH1 and HEXSH2 and the discharge superheat degrees TdSH1 and TdSH2 are controlled by appropriately increasing or decreasing the operation output of the blower 6 or the blower 106. Specifically, when the operation output of the blower 6 (106) is increased, the discharge superheat degree TdSH1 (TdSH2) and the outlet superheat degree HEXSH1 (HEXSH2) are increased, and when the operation output of the blower 6 (106) is reduced, the discharge superheat degree is increased.
- the increase / decrease in the operation output of the blower 6 (106) is determined using the decrease in the degree TdSH1 (TdSH2) and the outlet superheat degree HEXSH1 (HEXSH2).
- the heating capacity is impaired.
- the operation output of the blower 6 (106) is reduced too much in order to satisfy the superheat condition, the heating capacity is impaired.
- the operation output of the blower 6 (106) is increased too much, the noise value of the heat source device 51 (151) increases. Therefore, in the first embodiment, the following control is performed in order to prevent such inconvenience during the liquid leveling control.
- the first liquid leveling control means 100a is selected. Then, liquid leveling control using the blower 6 (106) is performed.
- the operation output of the blower 6 is lowered, and the discharge superheat degree TdSH1 is lowered to reduce the discharge.
- the suction pressure of the compressor 1 decreases, the refrigerant circulation amount decreases, and the heating capacity may be insufficient.
- the operation output of the blower 6 is stopped (that is, the current state is maintained), and liquid leveling control using frequency control of the compressor 1 (101) is performed to satisfy the superheat condition. This will correct the uneven distribution of refrigerant.
- the discharge superheat degree TdSH1 is controlled to be a predetermined value by increasing the operation output of the blower 6 and increasing the discharge superheat degree TdSH1, the operation of the blower 6 is performed.
- the noise value of the heat source device 51 increases due to the output being too large.
- the increase in the operation output of the blower 6 is stopped (that is, the current state is maintained), the liquid leveling control using the frequency control of the compressor 1 (101) is performed, and the superheat degree condition is set.
- FIG. 3 is a control flowchart during the heating operation of the air-conditioning apparatus according to Embodiment 1 of the present invention.
- the control means 100 predefines the outlet superheat degree HEXSH1 obtained by the heat exchanger outlet superheat degree calculating means 38 and the outlet superheat degree HEXSH2 obtained by the heat exchanger outlet superheat degree calculating means 138. It is determined whether or not the value is larger than the first specified value A (hereinafter referred to as specified value A) (S31).
- specified value A hereinafter referred to as specified value A
- the control unit 100 determines that the outlet superheat degrees HEXSH1 and HEXSH2 are both greater than the specified value A, the control unit 100 subsequently performs the following determination. That is, the control means 100 has the discharge superheat degree TdSH1 obtained by the discharge superheat degree calculating means 37 and the discharge superheat degree TdSH2 obtained by the discharge superheat degree calculating means 137 being the second prescribed values prescribed in advance. It is determined whether or not the value is larger than the value B (hereinafter, specified value B) (S32).
- control means 100 determines that the discharge superheat degrees TdSH1 and TdSH2 are both greater than the specified value B (S31; YES, S32; YES).
- the control means 100 returns to S31 and repeats the same processing. In this case, the control means 100 determines that there is no liquid refrigerant imbalance, and continues normal heating operation.
- control unit 100 determines that at least one of the outlet superheat degrees HEXSH1 and HEXSH2 is smaller than the specified value A (S31; NO), or at least one of the discharge superheat degrees TdSH1 and TdSH2 is equal to or less than the specified value B.
- S31; NO the specified value A
- TdSH1 and TdSH2 the discharge superheat degrees
- the first liquid leveling control means 100a compares the discharge superheat degree TdSH1 with the discharge superheat degree TdSH2 in order to determine which of the liquid refrigerant is biased (S33).
- the discharge superheat degree TdSH1 is larger than the discharge superheat degree TdSH2
- the first liquid leveling control unit 100a determines that the refrigerant is unevenly distributed on the heat source unit 151 side, and the discharge superheat degree TdSH1 is smaller than the discharge superheat degree TdSH2. In this case, it is determined that the liquid refrigerant is unevenly distributed on the heat source device 51 side.
- the first liquid leveling control unit 100a outputs the operation outputs of the blower 6 and the blower 106 so that the discharge superheat degree TdSH1 of the compressor 1 and the discharge superheat degree TdSH2 of the compressor 101 become predetermined values. Determine the increase or decrease.
- the discharge superheat degree TdSH1 and the discharge superheat degree TdSH2 are set to predetermined values by controlling the operation output of the blower so that the difference between the discharge superheat degree TdSH1 and the discharge superheat degree TdSH2 is equal to or less than a predetermined value specified in advance. Let it converge.
- the difference between the discharge superheat degree TdSH1 of the compressor 1 and the discharge superheat degree TdSH2 of the compressor 101 becomes smaller and converges to a predetermined value.
- the uneven distribution of the liquid refrigerant on the heat source device 151 side can be eliminated.
- the outlet superheat degree (that is, dryness) HEXSH1 and the outlet superheat degree (that is, dryness) HEXSH2 also changes following the change in the compressor discharge superheat degree, and the difference is similarly reduced.
- the difference can be made less than a specified value. It should be noted that which of the controls (a) to (c) depends on the setting of the predetermined value, and is not particularly limited.
- the blower 6 determines which of the following (a1) to (c1) is used for the control of the operation output of the blower 106.
- (A1) The operation output of the blower 6 is increased.
- (B1) The operation output of the blower 106 is decreased.
- (C1) The operation output of the blower 106 is decreased while the operation output of the blower 6 is increased.
- the change tendency of the refrigerant flow rate in the case of (a1) to (c1) is the same as that in the above (a) to (c).
- the refrigerant flow rate flowing to the heat source unit 51 side decreases, and (b1 ), The flow rate of the refrigerant flowing toward the heat source device 151 increases.
- the control of (a1) to (c1) depends on the setting of the predetermined value as in the above (a) to (c), and is not particularly limited.
- the increase / decrease in the operation output of the fan 6 and the fan 106 is determined as described above.
- control means 100 is each heat exchange of the heat source side heat exchanger 2 and the heat source side heat exchanger 102 based on the operation outputs Q1 and Q2 after increase / decrease in the operation output of the air blower 6 and the air blower 106 determined by S33.
- the amounts AK1 and AK2 and the total heat exchange amount AK of these are calculated by the heat exchange amount calculation means 39 (139).
- the control unit 100 determines whether or not the total heat exchange amount AK is within a preset allowable range. Specifically, it is determined whether or not the total heat exchange amount AK is larger than D1 [kW] and smaller than D2 [kW] (S34).
- the control unit 100 executes the liquid leveling control by the first liquid leveling control unit 100a. That is, liquid leveling control using the operation output control of the blower 6 (106) is performed according to the increase / decrease of the operation output determined in S33.
- the liquid leveling control using the second leveling control unit 100b that is, the frequency control of the compressor 1 (101) is performed. Decide that you want to control.
- the second liquid leveling control means 100b compares the discharge superheat degree TdSH1 with the discharge superheat degree TdSH2 in order to determine which of the liquid refrigerant is biased (S35). Since this comparison process is the same as S33, the comparison result of S33 may be inherited, and S35 may be omitted.
- the second liquid leveling control means 100b sets the compressor 1 and the compressor 101 so that the discharge superheat degree TdSH1 of the compressor 1 and the discharge superheat degree TdSH2 of the compressor 101 become predetermined values. Determine frequency increase / decrease.
- the frequency of the compressor 1 and the compressor 101 so that the difference between the discharge superheat degree TdSH1 of the compressor 1 and the discharge superheat degree TdSH2 of the compressor 101 is equal to or less than a predetermined value, The discharge superheat degree TdSH1 and the discharge superheat degree TdSH2 are converged to predetermined values.
- the frequency control of the compressor 1 and the compressor 101 is controlled as follows ( Determine which of A) to (C).
- the control of the frequency of the compressor 1 and the compressor 101 is as follows. (A1) to (C1) are determined.
- (A1) Increase the frequency of the compressor 1.
- (B1) The frequency of the compressor 101 is decreased.
- (C1) The frequency of the compressor 101 is decreased while the frequency of the compressor 1 is increased.
- the change tendency of the refrigerant flow rate in the case of (A1) to (C1) is the same as that in the above (A) to (C), and in the case of (A1), the refrigerant flow rate flowing to the heat source unit 51 side decreases, and (B1 ), The flow rate of the refrigerant flowing toward the heat source device 151 increases.
- the second liquid leveling control unit 100 b in performing the liquid leveling control using the frequency control of the compressor 1 (101), the second liquid leveling control unit 100 b The following determination is made to determine the amount of increase / decrease in the frequency of the compressor 1 (101) so as not to cause a decrease in capacity. That is, the refrigerant circulation amounts Gr1 and Gr2 of the heat source device 51 and the heat source device 151 and the total refrigerant circulation amount Gr thereof are calculated by the circulation amount calculating means 40 (140). And the 2nd liquid equalization control means 100b determines the increase / decrease amount of the compressor 1 (101), and prevents an excessive capability fall so that the total refrigerant
- the discharge superheat degree TdSH1 is larger than the discharge superheat degree TdSH2, one of the controls (A) to (C) is performed.
- the control (A) is performed, and only the compressor 1 is controlled to reduce the frequency and lower the discharge superheat degree TdSH1 to approach the discharge superheat degree TdSH2.
- the total refrigerant circulation amount Gr is calculated by the circulation amount calculating means 40 (140).
- the second liquid leveling control means 100b determines whether or not the total refrigerant circulation amount Gr is below a predetermined value E.
- the capacity is reduced when this control is performed. Therefore, another control is adopted. That is, only the compressor 1 adopts the control (C) described above, in which the frequency of the compressor 101 is increased while the frequency of the compressor 101 is increased, instead of the control (A) of decreasing the frequency. As a result, liquid leveling can be achieved while maintaining the ability.
- liquid leveling control using the operation output control of the blower 6 (106) but the compressor since liquid leveling control using frequency control of 1 (101) is performed, liquid leveling is possible while preventing a decrease in capacity. Further, liquid leveling can be performed while preventing an increase in noise of the heat source device.
- control is made to converge the discharge superheat degree TdSH1 and the discharge superheat degree TdSH2 to a predetermined value, but the control may be made to converge the outlet superheat degree HEXSH1 and the outlet superheat degree HEXSH2 to a predetermined value. .
- the imbalance detection means of the present invention is constituted by the discharge superheat degree calculation means 37, the discharge superheat degree calculation means 137, the heat exchanger outlet superheat degree calculation means 38, and the heat exchanger outlet superheat degree calculation means 138.
- the imbalance detection means of the present invention is not limited to a configuration that detects the presence or absence of imbalance based on the discharge superheat degree and the outlet superheat degree.
- the imbalance detection means may be constituted by the discharge superheat degree calculation means 37 and the discharge superheat degree calculation means 137, and the presence or absence of imbalance may be detected based only on the discharge superheat degree.
- the imbalance detecting means may be constituted by the heat exchanger outlet superheat degree calculating means 38 and the heat exchanger outlet superheat degree calculating means 138, and the presence or absence of imbalance may be detected based only on the outlet superheat degree. .
- adopted for a refrigerating-cycle apparatus is not specifically limited,
- coolants such as R410A, R32, R407C, R404A, HFO1234yf, may be used from natural refrigerant
- the configuration of the refrigerant circuit is not limited to that shown in the figure. That is, in the first embodiment, the shunt controller 52 is provided, and the liquid refrigerant separated by the gas-liquid separator 11 is passed through the inter-refrigerant heat exchanger 16 and the inter-refrigerant heat exchanger 17. It is good also as a structure which abbreviate
- the gas pipes 204 a and 204 a may be directly connected to the low pressure pipe 201, and the liquid pipes 203 a and 203 b may be directly connected to the high pressure pipe 202.
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Abstract
Description
図1は、本発明の実施の形態1に係る空気調和装置の冷媒回路を示す冷媒回路図である。この図1に基づいて、空気調和装置500の回路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。ここで、図1に示す空気調和装置500は熱源側ユニットである熱源機(熱源機51及び熱源機151)を備えており、各熱源機には重複する機能部品が搭載されている。このため、以下の説明においては、両熱源機を区別して説明する必要がない場合、熱源機51の機能部品の符号についてはそのまま記載し、熱源機151の機能部品の符号については括弧内に記載することとする。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、熱源機を3つ以上備えてもよいし、負荷側ユニットである利用側機を複数、備えていてもよい。
TdSH2=Td2-Tc2…(2)
ここで、
Tc1[℃]:吐出圧力検知手段31で検知された吐出圧力を飽和換算して求めた飽和温度
Tc2[℃]:吐出圧力検知手段131で検知された吐出圧力を飽和換算して求めた飽和温度
これ以降、圧縮機吐出過熱度はTdSHと示すこととする。
HEXSH2=Thex2-Te2…(4)
ここで、
Thex1[℃]:吸入圧力検知手段32で検知された吸入圧力を飽和換算して求めた飽和温度
Thex2[℃]:吸入圧力検知手段132で検知された吸入圧力を飽和換算して求めた飽和温度
これ以降、熱交換器出口過熱度はHEXSHと示すこととする。
AK2=C2×Q2…(6)
ここで、
AK1[kW]:熱源側熱交換器2の熱交換量
AK2[kW]:熱源側熱交換器102の熱交換量
C1:予め設定された熱源側熱交換器2の容積に応じた係数
C2:予め設定された熱源側熱交換器102の容積に応じた係数
Q1[kW]:送風機6の出力
Q2[kW]:送風機106の出力
Gr2[kg/h]=Ps2×F2…(8)
ここで、
Ps1[MPa]:吸入圧力検知手段32によって検知された圧力
Ps2[MPa]:吸入圧力検知手段132によって検知された圧力
F1[Hz]:圧縮機1の圧縮機出力
F2[Hz]:圧縮機101の圧縮機出力
ここで、本実施の形態1の均液制御の概要を説明する。
圧縮機1及び圧縮機101のそれぞれの冷媒吐出量に見合った割合で冷媒が分流する望ましい状態に近づけるためには、以下の過熱度条件を満足するようにすればよい。すなわち、圧縮機1の吐出過熱度TdSH1と圧縮機101の吐出過熱度TdSH2とを同等とすると共に、熱源側熱交換器2の出口過熱度HEXSH1と熱源側熱交換器102の出口過熱度HEXSH2とを所定値以上あるいは同等とすればよい。
暖房運転中、制御手段100は、熱交換器出口過熱度演算手段38で求められた出口過熱度HEXSH1と、熱交換器出口過熱度演算手段138で求められた出口過熱度HEXSH2とが、予め規定された第1規定値である値A(以下、規定値A)よりも大きいかどうかを判断する(S31)。
(b)送風機106の運転出力を増加させる。
(c)送風機6の運転出力を減少させつつ、送風機106の運転出力を増加させる。
この場合、熱源機51側の蒸発器熱交換容量が減少する。これにより、熱源側熱交換器2の出口過熱度、すなわち乾き度が減少すると共に圧縮機1の吐出過熱度TdSH1が減少する。そして、熱源機51側に流れる冷媒流量が増加する。
この場合、熱源機151側の蒸発器熱交換容量が増加する。これにより、熱源側熱交換器102の出口過熱度、すなわち乾き度が増加すると共に圧縮機101の吐出過熱度TdSH2が増加する。そして、熱源機151側に流れる冷媒流量が減少する。
この場合、圧縮機1の吐出過熱度TdSH1が減少する一方、圧縮機101の吐出過熱度TdSH2が増加し、吐出過熱度TdSH1と吐出過熱度TdSH2との差が小さくなる。
(b1)送風機106の運転出力を減少させる。
(c1)送風機6の運転出力を増加させつつ、送風機106の運転出力を減少させる。
(B)圧縮機101の周波数を増加させる。
(C)圧縮機1の周波数を減少させつつ、圧縮機101の周波数を増加させる。
圧縮機1の周波数を減少させた場合、圧縮機1から吐出される冷媒量が少なくなる。見方を変えれば、圧縮機1の周波数を減少させることで、周波数減少前に比べて圧縮機101から吐出される冷媒量が圧縮機1から吐出される冷媒量に対して相対的に増加する。よって、圧縮機1にとってみれば、圧縮機101から吐出されて圧縮機1側に戻ってくる冷媒量が多くなる。つまり、熱源機51側に流れる冷媒流量が増加し、圧縮機1の吐出過熱度TdSH1が小さくなる。
圧縮機101の周波数を増加させた場合は、圧縮機101から吐出される冷媒量が多くなる。よって、圧縮機101から吐出されて圧縮機101に戻ってくる冷媒量が少なくなる。つまり、熱源機151側に流れる冷媒流量が減少し、圧縮機101の吐出過熱度TdSH2が大きくなる。
この場合は、圧縮機1の吐出過熱度TdSH1が減少する一方、圧縮機101の吐出過熱度TdSH2が増加することで、吐出過熱度TdSH1と吐出過熱度TdSH2との差が小さくなる。
(B1)圧縮機101の周波数を減少させる。
(C1)圧縮機1の周波数を増加させつつ、圧縮機101の周波数を減少させる。
Claims (6)
- 圧縮機、熱源側熱交換器、アキュームレータ及び前記熱源側熱交換器に空気を供給する送風機をそれぞれ備えた複数の熱源機と、
複数の前記アキュームレータ間の液冷媒量の不均衡の有無を検知する不均衡検知手段と、
複数の前記熱源側熱交換器の合計熱交換量を演算する熱交換量演算手段と、
前記複数の熱源機の合計冷媒循環量を演算する循環量演算手段と、
前記不均衡検知手段で不均衡が有ると検知された場合に前記不均衡を是正する均液制御を行う制御手段とを備え、
前記制御手段は、
前記送風機の出力制御を行って前記均液制御を行う第1均液制御手段と、
前記圧縮機の周波数制御を行って前記均液制御を行う第2均液制御手段とを備え、
前記第2均液制御手段は、
前記圧縮機の周波数制御を用いた前記均液制御を行うにあたり、前記合計冷媒循環量が予め設定した所定量を下回らないように前記圧縮機の周波数の増減量を決定するものであり、
前記制御手段は、前記熱交換量演算手段の演算値が予め規定された許容範囲内の場合、前記第1均液制御手段を選択し、前記熱交換量演算手段の演算値が前記許容範囲外の場合、前記第2均液制御手段を選択して前記均液制御を行う空気調和装置。 - 前記圧縮機から吐出された冷媒の過熱度を演算する吐出過熱度演算手段を備え、
前記均液制御は、前記吐出過熱度演算手段で演算された、前記複数の熱源機のそれぞれにおける前記圧縮機から吐出された冷媒の過熱度を、所定値に収束させる制御である請求項1記載の空気調和装置。 - 前記圧縮機の吐出側における圧力を検知する圧力検知手段と、前記圧縮機から吐出された冷媒の温度を検知する温度検知手段とを備え、
前記吐出過熱度演算手段は、前記圧力検知手段の検知値及び前記温度検知手段の検知値に基づいて前記圧縮機から吐出された冷媒の過熱度を演算する請求項2記載の空気調和装置。 - 前記熱源側熱交換器から流出した冷媒の過熱度を演算する出口過熱度演算手段を備え、
前記均液制御は、前記出口過熱度演算手段で演算された、前記複数の熱源機のそれぞれにおける前記熱源側熱交換器から流出した冷媒の過熱度を、所定値に収束させる制御である請求項1記載の空気調和装置。 - 前記圧縮機の吸入側における冷媒の圧力を検知する圧力検知手段と、前記圧縮機に吸入される冷媒の温度を検知する温度検知手段とを備え、
前記出口過熱度演算手段は、前記圧力検知手段の検知値及び前記温度検知手段の検知値に基づいて前記熱源側熱交換器から流出した冷媒の過熱度を演算する請求項4記載の空気調和装置。 - 前記不均衡検知手段は、複数の前記圧縮機のそれぞれから吐出された冷媒の過熱度を、予め規定された第1規定値と比較すると共に、複数の前記熱源側熱交換器のそれぞれから流出した冷媒の過熱度を、予め規定された第2規定値と比較し、少なくとも1つの前記過熱度が、対応の前記規定値よりも小さい場合、不均衡有りと判断する請求項1~請求項5の何れか一項に記載の空気調和装置。
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