WO2016120937A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2016120937A1 WO2016120937A1 PCT/JP2015/006307 JP2015006307W WO2016120937A1 WO 2016120937 A1 WO2016120937 A1 WO 2016120937A1 JP 2015006307 W JP2015006307 W JP 2015006307W WO 2016120937 A1 WO2016120937 A1 WO 2016120937A1
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- WIPO (PCT)
- Prior art keywords
- oil
- refrigerant
- gas side
- indoor
- branch pipe
- Prior art date
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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
- 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
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
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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
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating 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
- 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
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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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
- F25B2313/031—Sensor arrangements
- F25B2313/0314—Temperature sensors near the indoor heat exchanger
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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
- F25B2313/031—Sensor arrangements
- F25B2313/0315—Temperature sensors near the outdoor heat exchanger
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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
- F25B2500/00—Problems to be solved
- F25B2500/16—Lubrication
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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
- F25B2500/00—Problems to be solved
- F25B2500/19—Calculation of parameters
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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
- F25B2600/00—Control issues
- F25B2600/19—Refrigerant outlet condenser temperature
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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
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
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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
- F25B2700/03—Oil level
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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
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction 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
- 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
Definitions
- the present invention relates to an air conditioner in which an outdoor unit and a plurality of indoor units are connected, and in particular, determines a target value of an evaporating temperature or a condensing temperature of a refrigerant circuit according to an indoor air conditioning load, and based on the target value.
- the present invention relates to the control of the oil recovery operation of the air conditioner that controls the operating capacity of the compressor.
- a refrigerant circuit that performs a vapor compression refrigeration cycle is configured by connecting an outdoor unit and a plurality of indoor units through a connecting pipe.
- a multi-type air conditioner is known (see, for example, Patent Document 1).
- the connecting pipe is branched from each of the gas side main pipe and liquid side main pipe connected to the outdoor unit, and the gas side main pipe and liquid side main pipe and connected to each indoor unit.
- the gas side branch pipe and the liquid side branch pipe are configured.
- the required capacity of the indoor unit is obtained, and the refrigerant temperature (evaporation temperature or condensation temperature) of the indoor heat exchanger is set to a target temperature corresponding to the required capacity.
- Energy saving is performed by controlling the operating capacity and the air volume of the indoor fan. That is, in the air conditioner of Patent Document 1, the refrigeration cycle is changed at the target evaporation temperature and the target condensation temperature while changing the target evaporation temperature and the target condensation temperature every predetermined time according to the required capacity of the indoor unit during the energy saving operation.
- the operating capacity of the compressor is controlled to operate.
- a part of the refrigerating machine oil stored in the compressor flows out of the compressor together with the refrigerant in order to lubricate the compression mechanism and bearings inside the compressor. Circulate through the refrigerant circuit.
- the refrigerating machine oil flows in the circuit together with the refrigerant.
- a part of the refrigerating machine oil is a heat exchanger tube of the heat exchanger. It adheres to the inner surface of the pipe and the inner surface of the refrigerant pipe.
- the target evaporation temperature may increase during cooling operation in order to save energy.
- the refrigerant circulation amount in the refrigerant circuit is reduced. Therefore, in an air conditioner to which indoor units having different capacities are connected, the refrigerant flow rate of the connected gas-side branch pipe becomes slow depending on the indoor unit.
- the refrigeration oil does not return to the compressor while adhering to the inner surface of the heat transfer pipe or the refrigerant pipe as described above, and the amount of refrigerant remaining in the gas side branch pipe increases.
- the amount of refrigerating machine oil stored in the machine is reduced.
- the compressor is operated in a state where the amount of refrigerating machine oil stored is small, and the compressor is likely to be poorly lubricated.
- the flow rate of the refrigerant in the gas side branch pipe is Whereas the flow rate may be slower than that required for oil recovery, conventionally, oil recovery has not been performed in consideration of the flow rate of the gas refrigerant in the gas side branch pipe.
- the present invention has been made in view of such problems, and an object of the present invention is to control the operation of the refrigerant circuit so that the refrigerant temperature of the indoor heat exchanger becomes a target temperature corresponding to the required capacity of the indoor unit.
- the lubrication failure in the compressor can be prevented by controlling the oil recovery operation in consideration of the flow rate of the gas refrigerant in the gas side branch pipe.
- the first aspect of the present disclosure includes a refrigerant circuit (11) configured by connecting an outdoor unit (20) and a plurality of indoor units (40) through communication pipes (71, 72), and the refrigerant circuit (11 ), And the communication pipe (71, 72) is connected to the outdoor unit (20) by the gas side main pipe (72a) and the liquid side main pipe (71a).
- the air provided with an air-conditioning capacity control unit (37a, 47a, 47b) for controlling the operation capacity of the refrigerant circuit (11) compressor based on It assumes a harmony device.
- the operation control unit (80) calculates the amount of refrigerating machine oil remaining in the communication pipe (71, 72) during operation, and the calculated value is a predetermined set amount.
- the oil recovery control unit (81) for performing an oil recovery operation for recovering the refrigeration oil in the refrigerant circuit (11) to the compressor (21), and the oil recovery control unit (81) As a reference value corresponding to the current value of the evaporating or condensing temperature of the circuit (11) and the lower limit flow velocity of the gas refrigerant necessary for the refrigerating machine oil to flow with the refrigerant without staying in the gas side branch pipe (72b).
- the gas side branch pipe In (72b) When it is determined that there is a gas side branch pipe (72b) that does not satisfy the lower limit flow velocity by comparing the set value of the evaporation temperature or condensation temperature determined for each indoor unit (40), the gas side branch pipe In (72b), it is judged that the refrigeration oil is stagnant and the gas It is characterized in having branch pipes oil retention amount calculation unit for calculating a residual amount of the refrigerating machine oil (72b) (82).
- the current value of the evaporation temperature target value or the current value of the evaporation temperature target value may be used as the “current value of the evaporation temperature or condensation temperature” to be compared with the reference value.
- the actual current value can also be used.
- the “target value” is a target value for the evaporation temperature or the condensation temperature when control is performed according to the air conditioning load in the room
- the “reference value” is the gas side branch pipe
- the “set value” is the value of the evaporation temperature or the condensation temperature used as the reference value
- the “set amount” is the value in the refrigerant pipe Represents a value for determining whether or not refrigeration oil has accumulated and oil recovery is required.
- the target value of the evaporating temperature or the condensing temperature of the refrigerant circuit (11) is determined according to the indoor air conditioning load, and the compressor operation of the refrigerant circuit (11) is performed based on the target value.
- the current value of the evaporating or condensing temperature of the refrigerant circuit (11) and the refrigerating machine oil it is necessary for the current value of the evaporating or condensing temperature of the refrigerant circuit (11) and the refrigerating machine oil to flow with the refrigerant in the gas side branch pipe (72b) without stagnation.
- the reference value of evaporation temperature or condensation temperature determined for each indoor unit (40) corresponding to the lower limit flow rate of the gas refrigerant was compared, and it was determined that there was a gas side branch pipe (72b) that did not satisfy the lower limit flow rate In this case, it is determined that the refrigerating machine oil stays in the gas side branch pipe (72b), and the refrigerating machine oil retention amount in the gas side branch pipe (72b) is calculated. When the calculated value exceeds a predetermined set amount, oil recovery operation is performed, and the refrigeration oil in the refrigerant circuit (11) is recovered by the compressor (21).
- the oil recovery control unit (81) has a gas side branch pipe according to one or a plurality of air volume levels that can be set for each indoor unit (40).
- a reference value storage unit (83) having a reference value of the lower limit flow velocity of (72b), wherein the oil retention amount calculation unit (82) is a refrigerant in the gas side branch pipe (72b) for each of the indoor units (40).
- the current value of the evaporating temperature or condensing temperature is compared with a reference value corresponding to the air flow level, and the presence or absence of a gas side branch pipe (72b) whose gas refrigerant flow rate is slower than the lower limit flow rate is determined. It is characterized by calculating the retention amount.
- the oil retention amount calculation unit (82) causes the gas side branch pipe (72b) whose current value of the evaporation temperature is higher than a set value. ) Is determined to calculate the retention amount of the refrigerating machine oil, and the oil recovery control unit (81) performs the oil recovery operation in the cooling cycle.
- this third mode during the cooling operation, it is determined whether or not the gas side branch pipe (72b) having a current value of the evaporation temperature higher than the set value is present, and the residence amount of the refrigerating machine oil is calculated. If it exceeds, oil recovery operation is performed with the cooling cycle kept.
- oil recovery operation by increasing the flow rate of the refrigerant, the refrigeration oil in the gas side branch pipe (72b) flows to the outdoor unit (20) through the gas side main pipe (72a) and goes to the compressor ( 21).
- the oil retention amount calculation unit (82) causes the gas side branch pipe (72b) whose current value of the condensation temperature is lower than a set value. ) Is determined to calculate the retention amount of the refrigerating machine oil, and the oil recovery control unit (81) switches to the cooling cycle and performs the oil recovery operation.
- the residence amount of the refrigerating machine oil is calculated by determining the presence or absence of the gas side branch pipe (72b) where the current value of the condensation temperature is lower than the set value. If exceeded, the oil recovery operation is performed by switching to the cooling cycle.
- the refrigerant flow in the gas side branch pipe (72b) flows in the direction of the outdoor unit (20) through the gas side main pipe (72a) by increasing the refrigerant flow rate. It goes and is collected by the compressor (21).
- the oil retention amount calculation unit (82) causes the gas side branch pipe (72b) whose current value of the condensation temperature is lower than a set value. ) To determine the retention amount of the refrigerating machine oil, and the oil recovery control unit (81) performs the oil recovery operation while maintaining the heating cycle.
- the gas side branch pipe (72b) having a current condensing temperature lower than the set value is present, and the residence amount of the refrigerating machine oil is calculated. If it exceeds, oil recovery operation is performed in the heating cycle.
- oil recovery operation is performed in the heating cycle, refrigeration oil in the gas side branch pipe (72b) flows from the indoor unit (40) through the liquid side main pipe (71a) by increasing the refrigerant flow rate. Go to the compressor (21) from the opposite direction to the cooling cycle.
- the oil recovery operation can be controlled in consideration of the flow rate of the gas refrigerant in the gas side branch pipe (72b), and the compressor (21 ) Can reliably prevent poor lubrication due to lack of oil.
- the current value of the refrigerant evaporation temperature or the condensation temperature of the gas side branch pipe (72b) and the indoor unit (40) to which the gas side branch pipe (72b) is connected are set. It is judged whether the refrigerating machine oil stays in the gas side branch pipe (72b) by comparing with the reference value of the lower limit flow velocity of the gas refrigerant according to one possible or the air flow level, and based on the result The amount of refrigeration oil staying in the gas side branch pipe (72b) is calculated, and if the stay amount exceeds the set amount, oil recovery operation is performed, so the flow rate of the gas refrigerant in the gas side branch pipe (72b) is taken into account.
- the reason is that if the capacity of the indoor unit (40) is the same, the evaporating temperature determined from the lower limit of the oil return flow rate increases as the air flow level increases, and the condensing temperature decreases as the air flow level increases. If you set a reference value according to the level and compare it with the current value, the accuracy of judgment will be higher than setting an average reference value for each indoor unit (40) and comparing it with the current value regardless of the air flow level. It is.
- the gas side branch pipe (72b) having a current value of the evaporation temperature higher than the set value is present, and the retention amount of the refrigerating machine oil is calculated. If the amount exceeds the set amount, the oil recovery operation is performed while the cooling cycle is maintained, so that the refrigeration oil staying in the gas side branch pipe (71b) can be reliably recovered to the compressor (21).
- the gas-side branch pipe (72b) whose current value of the condensation temperature is lower than the set value is present, and the retention amount of the refrigerating machine oil is calculated. Since the oil recovery operation is performed by switching to the cooling cycle when the amount exceeds the set amount, the refrigeration oil staying in the gas side branch pipe (71b) can be reliably recovered to the compressor (21).
- the presence or absence of the gas-side branch pipe (72b) whose current value of the condensation temperature is lower than the set value is determined to calculate the retention amount of the refrigerating machine oil.
- the oil recovery operation is performed while the heating cycle is maintained. Therefore, as in the fourth aspect of the present disclosure, the refrigerating machine oil retained in the gas side branch pipe (71b) is removed from the compressor ( 21) can be reliably collected.
- FIG. 1 is a refrigerant circuit diagram of the air-conditioning apparatus according to the present embodiment.
- FIG. 2 is a control block diagram of the air conditioner.
- FIG. 3 is a table showing an example of a reference value (evaporation temperature for each indoor unit) for calculating the oil retention amount of the gas side communication pipe during the cooling operation.
- FIG. 4 is a table showing an example of a reference value (condensation temperature for each indoor unit) for calculating the oil retention amount of the gas side communication pipe during the heating operation.
- FIG. 1 is a refrigerant circuit diagram of an air conditioner (10) according to the present embodiment.
- An air conditioner (10) is an apparatus used for air conditioning in a room such as a building by operating a vapor compression refrigeration cycle.
- the air conditioner (10) mainly includes an outdoor unit (20) as one heat source unit, and an indoor unit (40) as a plurality of units (four in this embodiment) connected in parallel to the outdoor unit (20). And a liquid side connecting pipe (71) and a gas side connecting pipe (72) as connecting pipes for connecting the outdoor unit (20) and the indoor unit (40).
- the outdoor unit (20) and the indoor unit (40) are connected to the liquid side communication pipe (71) and the gas side communication. It is comprised by connecting with piping (72).
- the connecting pipe (71, 72) includes a liquid side main pipe (71a) and a gas side main pipe (72a) connected to the outdoor unit (20), and a liquid side main pipe (71a) and a gas side main pipe ( 72a) is provided with a liquid side branch pipe (71b) and a gas side branch pipe (72b) branched from each of the indoor units (40).
- the indoor unit (40) is installed by embedding or hanging in a ceiling of a room such as a building or by hanging on a wall surface of the room.
- the indoor unit (40) is connected to the outdoor unit (20) via the liquid side communication pipe (71) and the gas side communication pipe (72), and constitutes a part of the refrigerant circuit (11).
- the indoor unit (40) has an indoor refrigerant circuit (11a) that constitutes a part of the refrigerant circuit (11).
- the indoor refrigerant circuit (11a) includes an indoor expansion valve (41) as an expansion mechanism and an indoor heat exchanger (42) as a use side heat exchanger.
- each indoor unit (40) is provided with an indoor expansion valve (41) as an expansion mechanism.
- the expansion mechanism may be provided in the outdoor unit (20).
- the connection unit may be provided independently of the indoor unit (40) and the outdoor unit (20).
- the indoor expansion valve (41) is an electric expansion valve connected to the liquid side of the indoor heat exchanger (42) in order to adjust the flow rate of the refrigerant flowing in the indoor refrigerant circuit (11a). It is also possible to block the passage of.
- the indoor heat exchanger (42) is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and functions as a refrigerant evaporator during cooling operation, It is a heat exchanger that cools and functions as a refrigerant condenser during heating operation to heat indoor air.
- the indoor heat exchanger (42) is a cross fin type fin-and-tube heat exchanger, but is not limited to this, and may be another type of heat exchanger. Good.
- the indoor unit (40) sucks indoor air into the unit, causes the indoor heat exchanger (42) to exchange heat with the refrigerant, and then supplies the indoor fan (43) as supply air to the room.
- the indoor fan (43) is a fan capable of adjusting the air volume of air supplied to the indoor heat exchanger (42) within a predetermined air volume range.
- the motor (43m) including a DC fan motor or the like. A centrifugal fan or a multiblade fan driven by the motor.
- an air volume fixed mode that sets three types of fixed air volume, that is, the weak wind with the smallest air volume, the strong wind with the largest air volume, and the intermediate wind between the weak wind and the strong wind; It is possible to set an air volume setting mode in which an air volume automatic mode that automatically changes between a weak wind and a strong wind according to the degree of superheat SH or the degree of supercooling SC is set by an input device such as a remote controller.
- an air volume fixing mode is fixed by the weak wind, and “automatic” is selected.
- the fan tap of the air volume of the indoor fan (43) is switched in three stages of “weak wind (L)”, “medium wind (M)”, and “strong wind (H)”. For example, there may be 10 stages.
- various sensors are provided in the indoor unit (40).
- a liquid side temperature sensor (44) for detecting the temperature of the refrigerant (condensation temperature Tc during heating operation or refrigerant temperature corresponding to the evaporation temperature Te during cooling operation) is provided. It has been.
- a gas side temperature sensor (45) for detecting the temperature of the refrigerant is provided on the gas side of the indoor heat exchanger (42).
- An indoor temperature sensor (46) for detecting the temperature of room air flowing into the unit (room temperature Tr) is provided on the indoor air inlet side of the indoor unit (40).
- thermistors are used for the liquid side temperature sensor (44), the gas side temperature sensor (45), and the room temperature sensor (46).
- the indoor unit (40) has an indoor side control unit (47) for controlling the operation of each unit constituting the indoor unit (40).
- the indoor control unit (47) has an air conditioning capability calculation unit (47a) that calculates the current air conditioning capability in the indoor unit (40), and the required evaporation required to demonstrate that capability based on the current air conditioning capability.
- a required temperature calculation unit (47b) for calculating the temperature Ter or the required condensation temperature Tcr.
- the indoor side control part (47) has a microcomputer, memory (47c), etc. provided in order to control an indoor unit (40), and operates an indoor unit (40) separately. Control signals etc. can be exchanged with the remote control (not shown) of the unit, and control signals etc. can be exchanged with the outdoor unit (20) via the transmission line (80a). It has become.
- the outdoor unit (20) is installed outside a building or the like, and is connected to the indoor unit (40) via the liquid side communication pipe (71) and the gas side communication pipe (72). ) And the refrigerant circuit (11).
- the outdoor unit (20) has an outdoor refrigerant circuit (11b) that constitutes a part of the refrigerant circuit (11).
- the outdoor refrigerant circuit (11b) includes a compressor (21), a four-way switching valve (22), an outdoor heat exchanger (23) as a heat source side heat exchanger, and an outdoor expansion valve ( 38), an accumulator (24), a liquid side closing valve (26), and a gas side closing valve (27).
- the compressor (21) is a compressor capable of adjusting the operating capacity, and in this embodiment, is a positive displacement compressor driven by a motor (21m) whose rotation speed is controlled by an inverter. In the present embodiment, only one compressor (21) is shown, but the present invention is not limited to this, and two or more compressors are connected in parallel according to the number of indoor units connected. Also good.
- the four-way switching valve (22) is a valve for switching the flow direction of the refrigerant, and during the cooling operation, the outdoor heat exchanger (23) is used as a refrigerant condenser compressed by the compressor (21), and In order for the indoor heat exchanger (42) to function as an evaporator for the refrigerant condensed in the outdoor heat exchanger (23), the discharge side of the compressor (21) and the gas side of the outdoor heat exchanger (23) And the suction side (specifically, the accumulator (24)) and the gas side connecting pipe (72) side of the compressor (21) are connected (cooling operation state: four-way switching valve (22 ) (See solid line).
- the four-way switching valve (22) is configured so that, during heating operation, the indoor heat exchanger (42) serves as a refrigerant condenser compressed by the compressor (21), and the outdoor heat exchanger (23) serves as indoor heat.
- the indoor heat exchanger (42) serves as a refrigerant condenser compressed by the compressor (21)
- the outdoor heat exchanger (23) serves as indoor heat.
- the discharge side of the compressor (21) and the gas side connecting pipe (72) side are connected and the suction side of the compressor (21) It is possible to connect the gas side of the outdoor heat exchanger (23) (heating operation state: see the broken line of the four-way switching valve (22) in FIG. 1).
- the outdoor heat exchanger (23) is a cross-fin type fin-and-tube heat exchanger, and is a device for exchanging heat with refrigerant using air as a heat source.
- the outdoor heat exchanger (23) is a heat exchanger that functions as a refrigerant condenser during cooling operation and functions as a refrigerant evaporator during heating operation.
- the outdoor heat exchanger (23) has a gas side connected to the four-way switching valve (22) and a liquid side connected to the outdoor expansion valve (38).
- the outdoor heat exchanger (23) is a cross-fin type fin-and-tube heat exchanger, but is not limited thereto, and may be another type of heat exchanger. Good.
- the outdoor expansion valve (38) is configured to control outdoor heat in the refrigerant flow direction in the refrigerant circuit (11) during the cooling operation in order to adjust the pressure and flow rate of the refrigerant flowing in the outdoor refrigerant circuit (11b).
- This is an electric expansion valve disposed on the downstream side of the exchanger (23) (in this embodiment, connected to the liquid side of the outdoor heat exchanger (23)).
- the outdoor unit (20) has an outdoor fan (28) as a blower for sucking outdoor air into the unit, exchanging heat with the refrigerant in the outdoor heat exchanger (23), and then discharging the air outside.
- the outdoor fan (28) is a fan capable of adjusting the air volume of the air supplied to the outdoor heat exchanger (23), and uses a propeller fan driven by a motor (28m) composed of a DC fan motor or the like. be able to.
- the liquid side shutoff valve (26) and gas side shutoff valve (27) are provided at the connection port with external equipment and piping (specifically, the liquid side connecting pipe (71) and gas side connecting pipe (72)). Valve.
- the liquid side shut-off valve (26) is disposed downstream of the outdoor expansion valve (38) and upstream of the liquid side connecting pipe (71) in the refrigerant flow direction in the refrigerant circuit (11) during cooling operation. It is possible to block the passage of the refrigerant.
- the gas side closing valve (27) is connected to the four-way switching valve (22).
- the outdoor unit (20) includes a suction pressure sensor (29) for detecting a suction pressure of the compressor (21) (that is, a refrigerant pressure corresponding to the evaporation pressure Pe during the cooling operation), a compressor A discharge pressure sensor (30) for detecting the discharge pressure of (21) (that is, a refrigerant pressure corresponding to the condensing pressure Pc during heating operation), and an intake temperature sensor (31) for detecting the intake temperature of the compressor (21) And a discharge temperature sensor (32) for detecting the discharge temperature of the compressor (21).
- An outdoor temperature sensor (36) for detecting the temperature of the outdoor air flowing into the unit (that is, the outdoor temperature) is provided on the outdoor air inlet side of the outdoor unit (20).
- the thermistor is used for the suction temperature sensor (31), the discharge temperature sensor (32), and the outdoor temperature sensor (36).
- the outdoor unit (20) has an outdoor control unit (37) that controls the operation of each unit constituting the outdoor unit (20).
- the outdoor side control unit (37) changes a target evaporation temperature Tet or a target condensation temperature Tct for controlling the operation capacity of the compressor (21) every predetermined time ( 37a) and is configured to perform energy-saving operation.
- the outdoor control unit (37) includes a microcomputer provided to control the outdoor unit (20), an inverter circuit that controls the memory (37b) and the motor (21m), and the like. Control signals and the like can be exchanged with the indoor side control section (47) of the unit (40) via the transmission line (80a).
- a controller (operation control unit) (80) that performs operation control of the entire air conditioner (10) is configured.
- Energy saving control during cooling operation is performed as follows. First, in the indoor side control part (47) of each indoor unit (40), the required evaporation temperature Ter is calculated from the temperature difference between the suction temperature and the set temperature, and transmitted to the outdoor side control part (37). Next, the outdoor side controller (37) of the outdoor unit (20) adopts a value having the lowest required evaporation temperature from the required evaporation temperatures Ter transmitted from the indoor units (40), and the control target. The target evaporation temperature Tet is determined as a value. The target evaporation temperature -Tet determined here is set as the current value of the evaporation temperature (current value of the refrigerant state value).
- a target condensation temperature Tct is determined by adopting a value having the highest required condensation temperature among the requested condensation temperatures calculated and transmitted by each indoor unit (40).
- the target condensation temperature Tct determined here is set as the current value of the condensation temperature (current value of the refrigerant state value).
- the controller (80) is connected so that it can receive detection signals from various sensors (29-32, 36, 44-46) as shown in FIG. 2 which is a control block diagram of the air conditioner (10). In addition, various devices and valves (21, 22, 28, 38, 41, 43) are connected based on these detection signals and the like. Various data are stored in the memory (37b, 47c) of the controller (80).
- the operation control unit (80) determines a target value for the evaporating temperature or the condensing temperature of the refrigerant circuit (11) according to an indoor air conditioning load, and the refrigerant based on the target value.
- An air conditioning capability control unit (37a, 47a, 47b) for controlling the operation capacity of the compressor (21) of the circuit (11) is provided.
- the air conditioning capability control unit (37a, 47a, 47b) includes the target value determination unit (37a), the air conditioning capability calculation unit (47a), and the required temperature calculation unit (47b).
- the controller (80) includes an oil recovery control unit (81).
- the oil recovery control unit (81) includes an oil retention amount calculation unit (82) and a reference value storage unit (83).
- the oil recovery control unit (81) calculates the amount of refrigerating machine oil staying in the communication pipe (71, 72) during operation and integrates the calculated value every predetermined time. When a predetermined set amount is exceeded, an oil recovery operation is performed in which the refrigeration oil in the refrigerant circuit (11) is recovered in the compressor (21).
- the oil retention amount calculation unit (82) causes the current value of the evaporation temperature target value or the condensation temperature target value of the refrigerant circuit (11) and the refrigerant oil to flow in the gas side branch pipe (72b) together with the refrigerant without retaining.
- the set value of evaporation temperature or condensation temperature which is a reference value determined for each indoor unit (40) corresponding to the lower limit flow rate of the gas refrigerant required for the gas side branch pipe ( When it is determined that there is 72b), it is determined that the refrigerating machine oil is retained in the gas side branch pipe (72b), and the refrigerating machine oil retention amount in the gas side branch pipe (72b) is calculated.
- the oil recovery control unit (81) obtains and accumulates the staying amount every predetermined time, and performs an oil recovery operation when the integrated value exceeds the set amount.
- the calculation of the oil retention amount per predetermined time by the oil retention amount calculation unit is calculated and integrated at more timings than the evaporation temperature determination process. Even when the target evaporation temperature is determined to be a predetermined value and the operating capacity control of the compressor (21) is being performed, the operating capacity of the compressor may vary, and thus at more timing in this way. By calculating the oil retention amount, it is possible to calculate a more accurate oil retention amount.
- the calculation of the oil retention amount per predetermined time by the oil retention amount calculation unit may be the same as or less than the calculation timing of the evaporation temperature determination process. If the calculation timing is the same or less, the number of processings can be reduced. Therefore, it is possible to use a cheaper microcomputer used for the outdoor control unit and the indoor control unit.
- the reference value storage unit (83) sets the evaporating temperature or the condensing temperature, which is the refrigerant state value indicating the refrigerant state corresponding to the branch pipe flow velocity lower limit value determined for each gas side branch pipe (72b), to the gas refrigerant flow velocity. As a reference value for determining.
- the outdoor unit (20) receives the model information of each connected indoor unit (40) and stores the capacity of each indoor unit (40) at the time of trial operation of the air conditioner. At this point, the outdoor unit (20) has the model information of each indoor unit (40) and the information for each gas side branch pipe (72b) connected thereto (refrigerant state value representing the branch pipe flow velocity lower limit). Have.
- the oil retention amount calculation unit (82) calculates the current value and the reference value of the refrigerant state value for each gas side branch pipe (72b) based on the stored information. To determine whether the flow rate of the gas refrigerant is slower than the lower limit value of the branch pipe flow rate, that is, whether the oil stays, and the gas flow rate determined to be slower than the lower limit value of the branch pipe flow rate The accumulated value is calculated by obtaining the oil retention amount in the side branch pipe (72b).
- the reference value storage unit (83) has the above lower limit flow velocity of the gas side branch pipe (72b) according to three air volume levels that can be set for each indoor unit (40). Has a reference value. Then, the oil retention amount calculation unit (82) sets the reference value according to the current value of the refrigerant evaporation temperature target value or the condensation temperature target value of the gas side branch pipe (72b) and the air flow level for each indoor unit (40). And determining whether or not there is a gas side branch pipe (72b) in which the flow rate of the gas refrigerant is lower than the lower limit flow rate, and the retention amount of the refrigerating machine oil is calculated.
- the controller (80) is configured to perform control to keep the evaporation temperature at the target value during the cooling operation.
- the oil retention amount calculation unit (82) calculates the retention amount of the refrigerating machine oil by determining the presence or absence of the gas side branch pipe (72b) where the current value of the evaporation temperature target value is higher than the set value (reference value). To do. This is because if the current value of the evaporation temperature target value is higher than the set value (reference value) during the cooling operation, it is determined that the flow rate of the refrigerant in the gas side branch pipe (72b) is slow. Further, the oil recovery control unit (81) performs the oil recovery operation while maintaining the cooling cycle.
- the current value of the evaporation temperature target value is compared with a set value (reference value).
- the reason why the evaporation temperature target value is used is that the actual evaporation temperature will eventually converge to the target value. In some cases, the actual evaporation temperature may be used instead of the evaporation temperature target value.
- the controller (80) is configured to perform control to keep the condensation temperature at the target value during the heating operation.
- the oil retention amount calculation unit (82) calculates the retention amount of the refrigerating machine oil by determining the presence or absence of the gas side branch pipe (72b) where the current value of the condensation temperature target value is lower than the set value. This is because if the current value of the condensation temperature target value is lower than the set value during the heating operation, it is determined that the flow rate of the refrigerant in the gas side branch pipe (72b) is slow.
- the oil recovery control unit (81) performs the oil recovery operation by switching to the cooling cycle. In this case as well, the condensing temperature target value is compared with the set value, but the actual condensing temperature may be used instead of the condensing temperature target value for the same reason as in the cooling operation.
- the communication pipes (71, 72) are refrigerant pipes that are installed on-site when the air conditioner (10) is installed at the installation location such as a building, and the installation location or combination of outdoor units and indoor units. Those having various lengths and pipe diameters are used depending on the installation conditions. For example, when a new air conditioner is installed, the air conditioner (10) is supplied with an appropriate amount of refrigerant according to the installation conditions such as the length of the connecting pipe (71, 72) and the pipe diameter. Need to be filled.
- the indoor refrigerant circuit (11a), the outdoor refrigerant circuit (11b), and the connecting pipes (71, 72) are connected to form the refrigerant circuit (11) of the air conditioner (10).
- the air conditioning apparatus (10) of this embodiment controls a four-way switching valve (22) by the controller (80) comprised from an indoor side control part (47) and an outdoor side control part (37).
- the operation of the outdoor unit (20) and the indoor unit (40) is controlled according to the operation load of each indoor unit (40), and the oil recovery operation is also performed. It has become.
- each indoor unit (40) performs indoor temperature control that brings the indoor temperature Tr close to the set temperature Ts set by the user using an input device such as a remote controller. Is going against.
- this indoor temperature control when the indoor fan (43) is set to the automatic air volume mode, the air volume of each indoor fan (43), and each of the indoor fans (43) so that the indoor temperature Tr converges to the set temperature Ts.
- the opening degree of the indoor expansion valve (41) is adjusted.
- the opening degree of each indoor expansion valve (41) is adjusted so that the indoor temperature Tr converges to the set temperature Ts.
- the “adjustment of the opening degree of each indoor expansion valve (41)” here refers to the control of the degree of superheat at the outlet of each indoor heat exchanger (42) in the case of cooling operation. In this case, the degree of supercooling at the outlet of each indoor heat exchanger (42) is controlled.
- the four-way switching valve (22) is in the state indicated by the solid line in FIG. 1, that is, the discharge side of the compressor (21) is connected to the gas side of the outdoor heat exchanger (23), and the compressor
- the suction side of (21) is connected to the gas side of the indoor heat exchanger (42) via the gas side shut-off valve (27) and the gas side communication pipe (72).
- the outdoor expansion valve (38) is fully opened.
- the liquid side closing valve (26) and the gas side closing valve (27) are in an open state.
- Each indoor expansion valve (41) adjusts the opening degree so that the superheat degree SH of the refrigerant at the outlet of the indoor heat exchanger (42) (that is, the gas side of the indoor heat exchanger (42)) becomes the target superheat degree SHt.
- the target superheat degree SHt is set to an optimum temperature value so that the room temperature Tr converges to the set temperature Ts within a predetermined superheat degree range.
- the superheat degree SH of the refrigerant at the outlet of each indoor heat exchanger (42) is detected by the liquid side temperature sensor (44) from the refrigerant temperature value detected by the gas side temperature sensor (45). It is detected by subtracting the temperature value (corresponding to the evaporation temperature Te).
- the superheat degree SH of the refrigerant at the outlet of each indoor heat exchanger (42) is not limited to being detected by the above-described method, and the suction pressure of the compressor (21) detected by the suction pressure sensor (29). May be detected by subtracting the saturation temperature value of the refrigerant from the refrigerant temperature value detected by the gas side temperature sensor (45).
- the compressor (21), the outdoor fan (28), and the indoor fan (43) are operated in the state of the refrigerant circuit (11), the low-pressure gas refrigerant is sucked into the compressor (21) and compressed and compressed. Gas refrigerant. Thereafter, the high-pressure gas refrigerant is sent to the outdoor heat exchanger (23) via the four-way switching valve (22), and is condensed by exchanging heat with the outdoor air supplied by the outdoor fan (28). And high pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the indoor unit (40) via the liquid-side closing valve (26) and the liquid-side connection pipe (71).
- the high-pressure liquid refrigerant sent to the indoor unit (40) is reduced to a pressure near the suction pressure of the compressor (21) by the indoor expansion valve (41) and becomes a low-pressure gas-liquid two-phase refrigerant. It is sent to the exchanger (42), exchanges heat with indoor air in the indoor heat exchanger (42), and evaporates to become a low-pressure gas refrigerant.
- This low-pressure gas refrigerant is sent to the outdoor unit (20) via the gas side connecting pipe (72), and through the gas side closing valve (27) and the four-way switching valve (22) to the accumulator (24 ). Then, the low-pressure gas refrigerant flowing into the accumulator (24) is again sucked into the compressor (21).
- the outdoor heat exchanger (23) is used as a condenser for the refrigerant compressed in the compressor (21), and the indoor heat exchanger (42) is used as an outdoor heat exchanger ( After cooling in 23), a cooling operation is performed to function as an evaporator for the refrigerant sent through the liquid side communication pipe (71) and the indoor expansion valve (41).
- the evaporation pressure Pe in all the indoor heat exchangers (42) is equal to the common pressure. Become. Conversely, if a mechanism for adjusting the refrigerant pressure is provided on the gas side of the indoor heat exchanger (42), the evaporation pressure in the indoor heat exchanger (42) can be arbitrarily changed.
- energy saving control can be performed in this cooling operation.
- the air conditioning capability calculation unit (47a) of the indoor side control unit (47) of each indoor unit (40) calculates the current air conditioning capability of the indoor unit (40).
- the air conditioning capacity calculator (47a) calculates the required capacity based on the set temperature.
- the controller (80) adjusts the operating capacity of the compressor (21), the opening of each indoor expansion valve (41), and the air volume of each indoor fan (43).
- each indoor unit (40) A value having the smallest required evaporation temperature is adopted among the required evaporation temperatures Ter transmitted from, and the target evaporation temperature Tet is determined as a control target value.
- the four-way switching valve (22) is in the state indicated by the broken line in FIG. It is connected to the gas side of the indoor heat exchanger (42), and the suction side of the compressor (21) is connected to the gas side of the outdoor heat exchanger (23).
- the outdoor expansion valve (38) adjusts the opening in order to reduce the refrigerant flowing into the outdoor heat exchanger (23) to a pressure at which the refrigerant can be evaporated in the outdoor heat exchanger (23) (that is, the evaporation pressure Pe). It has come to be.
- the liquid side closing valve (26) and the gas side closing valve (27) are opened.
- the opening of the indoor expansion valve (41) is adjusted so that the refrigerant subcooling degree SC at the outlet of the indoor heat exchanger (42) becomes the target subcooling degree SCt.
- the target supercooling degree SCt is set to an optimum temperature value so that the room temperature Tr converges to the set temperature Ts within the supercooling degree range specified according to the operation state at that time.
- the degree of refrigerant supercooling SC at the outlet of the indoor heat exchanger (42) is saturated with the discharge pressure Pd of the compressor (21) detected by the discharge pressure sensor (30) corresponding to the condensation temperature Tc. It is detected by converting to a temperature value and subtracting the refrigerant temperature value detected by the liquid side temperature sensor (44) from the saturation temperature value of this refrigerant.
- the compressor (21), the outdoor fan (28), and the indoor fan (43) are operated in the state of the refrigerant circuit (11), the low-pressure gas refrigerant is sucked into the compressor (21) and compressed and compressed. And is sent to the indoor unit (40) via the four-way switching valve (22), the gas-side closing valve (27), and the gas-side connecting pipe (72).
- the high-pressure gas refrigerant sent to the indoor unit (40) is subjected to heat exchange with the indoor air in the indoor heat exchanger (42) to be condensed into a high-pressure liquid refrigerant, and then the indoor expansion valve ( When passing through 41), the pressure is reduced according to the opening degree of the indoor expansion valve (41).
- the refrigerant that has passed through the indoor expansion valve (41) is sent to the outdoor unit (20) via the liquid side connection pipe (71), and then passes through the liquid side closing valve (26) and the outdoor expansion valve (38). After the pressure is further reduced, it flows into the outdoor heat exchanger (23). Then, the low-pressure gas-liquid two-phase refrigerant flowing into the outdoor heat exchanger (23) exchanges heat with the outdoor air supplied by the outdoor fan (28) to evaporate into a low-pressure gas refrigerant. It flows into the accumulator (24) via the path switching valve (22). Then, the low-pressure gas refrigerant flowing into the accumulator (24) is again sucked into the compressor (21). In the air conditioner (10), since there is no mechanism for adjusting the refrigerant pressure on the gas side of the indoor heat exchanger (42), the condensation pressure Pc in all the indoor heat exchangers (42) is equal to the common pressure. Become.
- energy saving control can be performed in this heating operation.
- the air conditioning capability calculation unit (47a) of the indoor side control unit (47) of each indoor unit (40) calculates the current air conditioning capability of the indoor unit (40).
- the air conditioning capacity calculator (47a) calculates the required capacity based on the set temperature.
- the controller (80) adjusts the operating capacity of the compressor (21), the opening of each indoor expansion valve (41), and the air volume of each indoor fan (43), and the condensation temperature is controlled by the same control as in the cooling operation. Driving is performed so as not to give more than necessary ability while keeping low.
- the compressor (21) when the compressor (21) is started for operation, it is always determined whether or not the oil recovery operation start condition is satisfied. Specifically, as described above, the amount of refrigerating machine oil staying in the gas side communication pipe (72) is calculated every predetermined time, and the calculated value every predetermined time is integrated, and the accumulated value of the staying amount Exceeds the set amount, an oil recovery operation for recovering the refrigeration oil in the refrigerant circuit (11) to the compressor (21) is performed on the assumption that an oil recovery operation start condition is satisfied. In this embodiment, at that time, not only the flow rate of the gas refrigerant in the gas side main pipe (72a) but also the flow rate of the gas refrigerant in each gas side branch pipe (72b) is estimated based on the evaporation temperature. When the lower limit value of the flow rate required for oil recovery is not satisfied, the integrated value is obtained from the amount of oil remaining in the gas side main pipe (72a) and the gas side branch pipe (72b).
- the above calculation result is used as the oil recovery start condition when the refrigeration oil retention amount in the gas side communication pipe (72) exceeds the set amount, and the amount of oil rising in the compressor (21) is greater than the predetermined value. This is because it is determined that the amount of refrigerating machine oil stored in the compressor (21) is less than a predetermined level.
- the oil recovery operation is performed if the start condition is satisfied in any of the compressors (21).
- the start condition for the oil recovery operation is also established when the set time of the timer has elapsed. For example, after the power is turned on, the compressor (21) has been operating for 2 hours or longer without the oil recovery operation being performed, or the compressor (21) has been operating for 8 hours or more since the previous oil recovery. In such a case, the start condition is established.
- the gas-side branch pipe (72b) and the gas-side main pipe The operation at which the flow rate of the refrigerant of (72a) is a predetermined high flow rate is continued for a predetermined time, and the oil is washed away by the gas refrigerant and recovered in the compressor (21).
- the indoor heat exchanger (42) which is an evaporator, performs wet operation control so that the refrigerant does not evaporate, whereby the refrigeration oil is recovered to the compressor with the liquid refrigerant.
- FIG. 3 is a table showing a set value of the evaporation temperature Te as a reference value corresponding to the lower limit flow velocity of oil recovery in four indoor units (40) having different capacities, and the values in this table are the reference value storage unit ( 83).
- the evaporation temperature Te corresponding to the lower limit flow rate of oil recovery is obtained from the table of FIG. And let the minimum value in that be the lower limit flow velocity of oil recovery.
- the indoor unit of the thermo-on is an indoor unit with a capacity Q1, an indoor unit with a capacity Q2, an indoor unit with a capacity Q3, and an indoor unit with a capacity Q4 (Q1 ⁇ Q2 ⁇ Q3 ⁇ Q4)
- the capacity Q1 If the fan tap of the indoor unit is L, the fan tap of the indoor unit with the capacity Q2 is M, the fan tap of the indoor unit with the capacity Q3 is H, and the fan tap of the indoor unit with the capacity Q4 is M,
- the minimum value of the evaporation temperature Te serving as the reference value is 11 ° C.
- the information regarding the fan tap of each indoor unit shall be received from the indoor unit each time the oil retention amount is calculated.
- the flow rate (retention amount) of oil flowing through the gas side branch pipe (72b) is calculated.
- the retention amount is obtained by multiplying the value A by the refrigerant circulation amount per unit time ⁇ T, the oil rising rate of the compressor, the refrigerant solubility, and the like.
- A is a value indicating the ratio of the thermo-on indoor units whose oil recovery lower limit flow rate is not satisfied with respect to the total capacity of all the thermo-on indoor units
- A Oil recovery lower limit flow velocity Thermo-on indoor unit total capacity / thermo-on indoor unit total capacity.
- the target value Tet of the evaporation temperature is 14.5 in a state where the fan tap of the indoor unit (40) of the thermo-on is set to (Q1 (L), Q2 (M), Q3 (H), Q4 (H)).
- ⁇ T 20. Therefore, the accumulated amount of oil is calculated by obtaining the oil retention amount from these numerical values.
- the present value of the evaporation temperature target value is compared with the reference value (set value) for each gas side branch pipe (72b) (considering the flow rate of the gas refrigerant), and the amount of oil retention And the integrated value is obtained therefrom.
- the amount of refrigerating machine oil remaining in the gas side main pipe (72a) is the main pipe flow rate. Calculated as internal oil retention. Even if the flow rate of the gas refrigerant in the gas side main pipe (72a) is faster than the lower limit value of the main pipe flow rate, the flow rate of the gas refrigerant in the gas side branch pipe (72b) is lower than the preset lower limit value of the branch pipe flow rate.
- the oil retention amount calculating unit (82) calculates the oil retention amount of the gas side main pipe (72a) and the gas side branch pipe (72b), and the integrated value is calculated from these values. When the calculated integrated value exceeds the set amount, an oil recovery operation is performed, and the refrigeration oil in the refrigerant circuit (11) is recovered by the compressor (21).
- the oil retention amount may be calculated for each compressor, and the oil retention operation may be performed by obtaining the total retention amount from these retention amounts.
- the accumulated value of the oil retention amount is reset and normal operation is performed, and the oil retention amount in the gas side communication pipe (72) is newly calculated / integrated, and the next oil recovery operation is performed. Prepare for.
- the oil retention amount in the gas side communication pipe (72) is calculated based on the table of FIG. 4, and the value is integrated every predetermined time ⁇ T to obtain the integrated value of the oil retention amount.
- the condensation temperature target value Tct is lower than the reference value in Table 4, the flow rate of the gas refrigerant is slow, and the point that it is determined that the refrigeration oil is not recovered by the compressor (21) is different from that in the cooling operation.
- the above integrated value is obtained in the same manner as in the cooling operation.
- the refrigerant flows through the gas side connecting pipe (72) toward the indoor heat exchanger (42), and it is not easy to recover the oil to the compressor (21) in the refrigeration cycle as it is. Then, the oil recovery operation is performed by switching to the cooling cycle so that the gas refrigerant is sucked into the compressor (21). By doing in this way, the oil collected in the gas side connection piping can be easily recovered even during heating operation.
- the current value of the refrigerant evaporation temperature target value or the condensation temperature target value of the gas side branch pipe (72b) and the indoor unit (40) to which the gas side branch pipe (72b) is connected By comparing with the reference value of the lower limit flow velocity of the gas refrigerant according to the multiple air flow levels that can be set in, it is determined whether the refrigeration oil is staying in the gas side branch pipe (72b) and based on the result Since the refrigeration oil retention amount in the gas side branch pipe (72b) is calculated and the oil recovery operation is performed when the retention amount exceeds the set amount, the flow rate of the gas refrigerant in the gas side branch pipe (72b) It becomes possible to improve the accuracy of control of the oil recovery operation performed in consideration, and it is possible to more reliably prevent poor lubrication in the compressor (21).
- the control will be accurate if the capacity of the indoor unit (40) is the same, the evaporation temperature and condensation temperature determined from the lower limit of the oil recovery flow rate will be the airflow level. This is because if the reference value is set for each air volume level, the accuracy of determining whether or not oil recovery is necessary is higher than setting one average value as the reference value.
- the retention amount of the refrigerating machine oil is calculated by determining the presence or absence of the gas side branch pipe (72b) in which the current value of the evaporation temperature target value is higher than the set value. If the amount exceeds the set amount, the oil recovery operation is performed while the cooling cycle is maintained, so that the refrigeration oil staying in the gas side branch pipe (71b) can be reliably recovered to the compressor (21).
- the retention amount of the refrigerating machine oil is calculated by determining the presence or absence of the gas side branch pipe (72b) in which the current value of the condensation temperature target value is lower than the set value. Since the oil recovery operation is performed by switching to the cooling cycle when the amount exceeds the set amount, the refrigeration oil staying in the gas side branch pipe (71b) can be reliably recovered to the compressor (21).
- the presence or absence of the gas side branch pipe (72b) where the current value of the condensation temperature target value is lower than the set value is determined to calculate the retention amount of the refrigerating machine oil.
- the oil recovery operation is performed by switching to the cooling cycle, but the oil recovery operation may be performed in the heating cycle.
- refrigeration oil in the gas side branch pipe (72b) flows from the indoor unit (40) through the liquid side main pipe (71a) by increasing the refrigerant flow rate. It goes to the compressor (21) from the opposite direction to the cooling cycle.
- the reference values of the evaporation temperature shown in FIG. 3 and the condensation temperature shown in FIG. 4 are merely examples, and may be appropriately changed according to the configuration of the air conditioner. Moreover, although the example which sets 3 types of fan taps was shown in FIG.3 and FIG.4, you may change, for example to 10 types.
- an outdoor unit and a plurality of indoor units are connected, and a target value of the evaporating temperature or condensing temperature of the refrigerant circuit is determined according to an indoor air conditioning load, and based on the target value. This is useful for controlling the oil recovery operation of the air conditioner that controls the operating capacity of the compressor.
- Air conditioner 11 Refrigerant circuit 20 Outdoor unit 37a Target value decision unit (air conditioning capability control unit) 40 Indoor unit 47a Air conditioning capacity calculator (air conditioning capacity controller) 47b Required temperature calculator (air conditioning capability controller) 71 Liquid side connection pipe 71a Liquid side main pipe 71b Liquid side branch pipe 72 Gas side connection pipe 72a Gas side main pipe 72b Gas side branch pipe 80 Operation control unit (controller) 81 Oil recovery control unit 82 Oil retention amount calculation unit 83 Reference value storage unit
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Abstract
Description
図1は、本実施形態に係る空気調和装置(10)の冷媒回路図である。空気調和装置(10)は、蒸気圧縮式冷凍サイクルの運転を行うことによって、ビル等の室内の冷暖房に使用される装置である。空気調和装置(10)は、主として、1台の熱源ユニットとしての室外ユニット(20)と、それに並列に接続された複数台(本実施形態では4台)の利用ユニットとしての室内ユニット(40)と、室外ユニット(20)と室内ユニット(40)とを接続する連絡配管としての液側連絡配管(71)及びガス側連絡配管(72)とを備えている。すなわち、本実施形態の空気調和装置(10)の蒸気圧縮式の冷媒回路(11)は、室外ユニット(20)と、室内ユニット(40)とが、液側連絡配管(71)及びガス側連絡配管(72)で接続されることによって構成されている。
室内ユニット(40)は、ビル等の室内の天井に埋め込みや吊り下げ等により、または、室内の壁面に壁掛け等により設置されている。室内ユニット(40)は、液側連絡配管(71)及びガス側連絡配管(72)を介して室外ユニット(20)に接続されており、冷媒回路(11)の一部を構成している。
室外ユニット(20)は、ビル等の室外に設置されており、液側連絡配管(71)及びガス側連絡配管(72)を介して室内ユニット(40)に接続されており、室内ユニット(40)とともに冷媒回路(11)を構成している。
連絡配管(71,72)は、空気調和装置(10)をビル等の設置場所に設置する際に、現地にて施工される冷媒管であり、設置場所や、室外ユニットと室内ユニットとの組み合わせ等の設置条件に応じて種々の長さや配管径を有するものが使用される。そして、例えば、新規に空気調和装置を設置する場合には、空気調和装置(10)には、連絡配管(71,72)の長さや管径等の設置条件に応じた適正な量の冷媒を充填する必要がある。
次に、本実施形態の空気調和装置(10)の運転動作について説明する。
まず、冷房運転について、図1を用いて説明する。
次に、暖房運転について、図1を用いて説明する。
冷房運転時の油回収運転は以下のようにして行われる。
A=油回収下限流速サーモオン室内ユニット合計容量/サーモオン室内ユニット合計容量
で求められる。ガス側主配管(72a)で流速不足が生じている場合は、すべての室内ユニットで流速不足になっているので、A=1となる。
A=(Q1+Q2)/(Q1+Q2+Q3+Q4)
となる。また、積算を20秒ごとに行うとすると、ΔT=20であるので、これらの数値から油の滞留量を求めて積算値を算出する。このように、本実施形態では、各ガス側分岐配管(72b)について蒸発温度目標値の現在値と基準値(設定値)を比較して(ガス冷媒の流速を考慮して)油の滞留量を求め、そこから積算値を求めるようにしている。
本実施形態によれば、省エネルギー運転を行うときに、ガス側分岐配管(72b)のガス冷媒の流速を考慮して油回収運転の制御を行うことが可能となり、圧縮機(21)において油不足による潤滑不良を確実に防止できる。
上記実施形態については、以下のような構成としてもよい。
11 冷媒回路
20 室外ユニット
37a 目標値決定部(空調能力制御部)
40 室内ユニット
47a 空調能力演算部(空調能力制御部)
47b 要求温度演算部(空調能力制御部)
71 液側連絡配管
71a 液側主配管
71b 液側分岐配管
72 ガス側連絡配管
72a ガス側主配管
72b ガス側分岐配管
80 運転制御部(コントローラ)
81 油回収制御部
82 油滞留量算出部
83 基準値格納部
Claims (5)
- 室外ユニット(20)と複数の室内ユニット(40)とが連絡配管(71,72)で接続されて構成された冷媒回路(11)と、該冷媒回路(11)の動作を制御する運転制御部(80)とを備え、
上記連絡配管(71,72)が、室外ユニット(20)に接続されたガス側主配管(72a)及び液側主配管(71a)と、該ガス側主配管(72a)及び液側主配管(71a)のそれぞれから分岐して各室内ユニット(40)に接続されたガス側分岐配管(72b)及び液側分岐配管(71b)とを備え、
上記運転制御部(80)が、室内の空調負荷に応じて上記冷媒回路(11)の蒸発温度または凝縮温度の目標値を決定し、その目標値に基づいて上記冷媒回路(11)の圧縮機(21)の運転容量を制御する空調能力制御部(37a,47a,47b)を備えた空気調和装置であって、
上記運転制御部(80)は、運転中に上記連絡配管(71,72)に滞留する冷凍機油の滞留量を算出し、その算出値が予め定められた設定量を超えると上記冷媒回路(11)内の冷凍機油を上記圧縮機(21)に回収する油回収運転を行う油回収制御部(81)を備え、
上記油回収制御部(81)は、上記冷媒回路(11)の蒸発温度または凝縮温度の現在値と、上記ガス側分岐配管(72b)内を冷凍機油が滞留せずに冷媒とともに流れるのに必要なガス冷媒の下限流速に対応する基準値として上記室内ユニット(40)ごとに定められた蒸発温度または凝縮温度の設定値とを比較し、上記下限流速を満たさないガス側分岐配管(72b)があると判定された場合はそのガス側分岐配管(72b)に冷凍機油が滞留していると判断して、該ガス側分岐配管(72b)の冷凍機油の滞留量を算出する油滞留量算出部(82)を有していることを特徴とする空気調和装置。 - 請求項1において、
上記油回収制御部(81)は、上記室内ユニット(40)ごとに設定可能な一つまたは複数の風量レベルに応じてガス側分岐配管(72b)の上記下限流速の基準値を有する基準値格納部(83)を備え、
上記油滞留量算出部(82)は、上記室内ユニット(40)ごとにガス側分岐配管(72b)の冷媒の蒸発温度または凝縮温度の現在値と風量レベルに応じた基準値とを比較し、ガス冷媒の流速が上記下限流速よりも遅いガス側分岐配管(72b)の有無を判定して上記冷凍機油の滞留量を算出することを特徴とする空気調和装置。 - 請求項1または2において、
冷房運転時、上記油滞留量算出部(82)は、蒸発温度の現在値が設定値よりも高いガス側分岐配管(72b)の有無を判定して上記冷凍機油の滞留量を算出し、油回収制御部(81)は、冷房サイクルのままで油回収運転を行うことを特徴とする空気調和装置。 - 請求項1または2において、
暖房運転時、上記油滞留量算出部(82)は、凝縮温度の現在値が設定値よりも低いガス側分岐配管(72b)の有無を判定して上記冷凍機油の滞留量を算出し、油回収制御部(81)は、冷房サイクルに切り換えて油回収運転を行うことを特徴とする空気調和装置。 - 請求項1または2において、
暖房運転時、上記油滞留量算出部(82)は、凝縮温度の現在値が設定値よりも低いガス側分岐配管(72b)の有無を判定して上記冷凍機油の滞留量を算出し、油回収制御部(81)は、暖房サイクルのままで油回収運転を行うことを特徴とする空気調和装置。
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