WO2016117128A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2016117128A1 WO2016117128A1 PCT/JP2015/051919 JP2015051919W WO2016117128A1 WO 2016117128 A1 WO2016117128 A1 WO 2016117128A1 JP 2015051919 W JP2015051919 W JP 2015051919W WO 2016117128 A1 WO2016117128 A1 WO 2016117128A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- compressor
- temperature
- flow rate
- state
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
-
- 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
-
- 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
- F25B2400/16—Receivers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/23—Separators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2515—Flow valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
-
- 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
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
-
- 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
- F25B2700/2104—Temperatures of an indoor room or compartment
-
- 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
-
- 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
- F25B2700/2108—Temperatures of a receiver
-
- 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
- F25B2700/2113—Temperatures of a suction accumulator
-
- 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
-
- 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
-
- 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
- F25B2700/2116—Temperatures of a condenser
- F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
-
- 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
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
Definitions
- the present invention relates to an air conditioner having a refrigerant circuit for circulating a refrigerant.
- a refrigerant container for storing excess refrigerant is installed so that a refrigerant shortage does not occur due to a change in operating conditions in the refrigerant circuit.
- An example of the refrigerant container is an accumulator that is installed on the suction side of the compressor and temporarily stores the refrigerant that has flowed out of the evaporator.
- receivers and the like that are arranged at positions where the medium-pressure refrigerant flows and temporarily store the refrigerant flowing out of the condenser or the evaporator.
- the accumulator installed on the suction side of the compressor is required to have a function of storing surplus refrigerant. Furthermore, the accumulator suppresses the liquid back amount in order to prevent an excessive state of the liquid back into which the liquid refrigerant flows into the compressor, and stores a large amount of refrigeration oil that has flowed out of the compressor together with the refrigerant inside the container. There is also a need for a function to reliably return oil to the compressor.
- the surplus refrigerant amount varies depending on operating conditions such as outside air conditions and the operating frequency of the compressor. Generally, under the low evaporation temperature condition, the refrigerant circulation amount is small and the surplus refrigerant amount tends to be large. On the other hand, under the high evaporation temperature condition, the refrigerant circulation amount is large and the surplus refrigerant amount tends to be small.
- the refrigeration oil used together with the refrigerant in the air conditioner reaches a certain temperature or higher, the oil density becomes smaller than the refrigerant density, and two-layer separation of the liquid refrigerant and the refrigeration oil occurs.
- the temperature at which this two-layer separation occurs is referred to as a two-layer separation temperature, and the two-layer separation temperature varies depending on the combination of refrigerant and refrigerator oil used. For example, when ether oil (PVE) is used as the R410A refrigerant, the two-layer separation temperature becomes ⁇ 50 ° C. or lower, whereas when PVE is used as the R32 refrigerant, the two-layer separation temperature increases to about ⁇ 5 ° C.
- PVE ether oil
- a conventional air conditioner has a sealed container, an inlet pipe and an outlet pipe that open in the sealed container, and one end connected to an outlet pipe outside the sealed container, and a plurality of oil recovery holes are formed along the vertical direction. And an accumulator having a first oil return pipe having one end connected to an outlet pipe outside the sealed container and the other end opened to the bottom of the sealed container. And the said air conditioning apparatus provides a 1st on-off valve in either of the connection parts of a 1st oil return pipe and an exit pipe, and it is 2nd in any of the connection parts of a porous pipe and an exit pipe in the exterior of an airtight container. An on-off valve is provided, and two-layer separation detection control means for controlling the on-off valve by detecting the state of the refrigerating machine oil and the refrigerant staying in the sealed container with at least one of the refrigerant pressure and temperature is provided.
- the first oil return pipe and the porous pipe are connected to the outlet pipe outside the sealed container, and the first open / close valve and the second open / close valve are provided between the sealed container and each connecting portion. These on-off valves are controlled to be opened and closed by the two-layer separation detection control means.
- the air conditioner performs the necessary amount of oil return while suppressing the excessive inflow of the liquid refrigerant to the compressor even when the two-layer separation occurs by such opening / closing control.
- the conventional air conditioner can control the amount of liquid refrigerant flowing into the compressor and the amount of oil return by opening and closing the on-off valve, it can change the operating condition of the refrigerant circuit or the operating conditions such as outside air conditions. Accordingly, there is no means for adjusting the valve opening. For this reason, the air conditioner has a problem that the flow rate control of the refrigerant flow rate and the oil return amount appropriate for the operating conditions is not performed, and the performance and reliability of the air conditioner deteriorate.
- the present invention has been made in order to solve the above-described problems, and an appropriate refrigerant flow rate and compressor that always meet the operating conditions regardless of changes in the operating conditions such as the operating state of the refrigerant circuit and the outside air conditions.
- An object of the present invention is to obtain an air conditioner that can secure the amount of oil returned to the tank and that can prevent performance degradation and reliability deterioration.
- An air conditioner according to the present invention includes a refrigerant circuit in which a compressor, a heat source side heat exchanger, a pressure reducing device, a use side heat exchanger, and a refrigerant container are sequentially connected via a pipe, and one end inside the refrigerant container.
- a bypass pipe inserted and the other end connected to the suction side pipe of the compressor; a flow rate adjusting valve provided in the bypass pipe; a first detector for detecting a refrigerant temperature in the refrigerant container; A storage unit that stores information on a two-layer separation temperature of the refrigerant and the refrigerating machine oil; a determiner that compares the refrigerant temperature and the two-layer separation temperature to determine a two-layer separation state of the refrigerant and the refrigerating machine oil; A second detector for detecting an intake refrigerant state of the compressor; and a control unit for adjusting an opening of the flow rate adjusting valve based on the two-layer separation state and the intake refrigerant state.
- the air conditioner includes a determination unit that determines the two-layer separation state in the refrigerant container, and a control device that adjusts the opening of the flow rate adjustment valve based on the determination result of the two-layer separation state.
- FIG. 1 is a configuration diagram of a refrigerant circuit schematically showing an air conditioner 100 according to an embodiment of the present invention.
- the air conditioning apparatus 100 is an apparatus used for indoor air conditioning by performing a vapor compression refrigeration cycle operation.
- the air conditioning apparatus 100 includes a heat source unit A and a plurality of utilization units B.
- the case of one usage unit B will be described as an example.
- the heat source unit A and the plurality of utilization units B are connected via a liquid connection pipe 6 and a gas connection pipe 9 which are refrigerant communication pipes.
- refrigerant used in the air conditioner 100 examples include an HFC refrigerant such as R410A, R407C, R404A, and R32, an HFO refrigerant such as R1234yf / ze, an HCFC refrigerant such as R22 and R134a, or carbon dioxide (CO2), carbonized.
- HFC refrigerant such as R410A, R407C, R404A, and R32
- HFO refrigerant such as R1234yf / ze
- HCFC refrigerant such as R22 and R134a
- CO2 carbon dioxide
- the usage unit B is installed by being embedded in an indoor ceiling, suspended, or wall-mounted on an indoor wall surface. As described above, the utilization unit B is connected to the heat source unit A via the liquid connection pipe 6 and the gas connection pipe 9 to constitute a part of the refrigerant circuit.
- the utilization unit B constitutes an indoor refrigerant circuit that is a part of the refrigerant circuit, and includes an indoor blower 8 and an indoor heat exchanger 7.
- the indoor heat exchanger 7 corresponds to the “use side heat exchanger” in the present invention.
- the indoor heat exchanger 7 is composed of, for example, a cross fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.
- the indoor heat exchanger 7 functions as a refrigerant evaporator during cooling operation to cool indoor air, and functions as a refrigerant condenser during heating operation to heat indoor air.
- the indoor air blower 8 is a fan capable of changing the flow rate of air supplied to the indoor heat exchanger 7, for example, a centrifugal fan driven by a DC motor (not shown), a multiblade fan, or the like. It is configured.
- the indoor air blower 8 sucks room air into the utilization unit B, and exchanges heat with the refrigerant in the indoor heat exchanger 7. And the indoor air blower 8 supplies the air which heat-exchanged indoors as supply air.
- a liquid side temperature sensor 205 that detects the temperature of the refrigerant in the liquid state or the gas-liquid two-phase state is provided on the liquid side of the indoor heat exchanger 7.
- the temperature of the refrigerant in the liquid state or the gas-liquid two-phase state includes the refrigerant temperature corresponding to the supercooled liquid temperature Tco during the heating operation or the evaporation temperature Te during the cooling operation.
- the indoor heat exchanger 7 is provided with a gas side temperature sensor 207 that detects the temperature of the refrigerant in the gas-liquid two-phase state. As the temperature of the refrigerant in the gas-liquid two-phase state, there is a refrigerant temperature corresponding to the condensation temperature Tc during the heating operation or the evaporation temperature Te during the cooling operation.
- an indoor temperature sensor 206 for detecting the temperature of the indoor air flowing into the unit is provided on the indoor air inlet side of the usage unit B.
- the liquid side temperature sensor 205, the gas side temperature sensor 207, and the room temperature sensor 206 are all composed of thermistors.
- the operation of the indoor air blower 8 is controlled by a control device 30 (operation control means).
- Heat source unit A Next, a detailed configuration of the heat source unit A will be described.
- the heat source unit A is installed outdoors and is connected to the utilization unit B through the liquid connection pipe 6 and the gas connection pipe 9 and constitutes a part of the refrigerant circuit.
- the heat source unit A includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an outdoor air blower 4, a decompressor 5, an accumulator 11, and a flow rate adjustment valve 13.
- the outdoor heat exchanger 3 corresponds to the “heat source side heat exchanger” in the present invention.
- the accumulator 11 corresponds to a “refrigerant container” in the present invention.
- Compressor 1 is a device capable of varying the operating capacity (frequency), and here uses a positive displacement compressor driven by a motor (not shown) controlled by an inverter.
- the compressor 1 is only one here, this invention is not limited to this, Two or more compressors 1 are connected in parallel according to the number of connected use units B, etc. It may be.
- the four-way valve 2 is a valve having a function of switching the direction of refrigerant flow.
- the four-way valve 2 connects the discharge side of the compressor 1 and the gas side of the outdoor heat exchanger 3, and connects the refrigerant flow so that the suction side of the compressor 1 and the gas connection pipe 9 side are connected.
- the path is switched (broken line of the four-way valve 2 in FIG. 1).
- the outdoor heat exchanger 3 functions as a condenser for the refrigerant compressed in the compressor 1
- the indoor heat exchanger 7 is a refrigerant that is condensed in the outdoor heat exchanger 3. It functions as an evaporator.
- the four-way valve 2 connects the discharge side of the compressor 1 and the gas connection pipe 9 side, and connects the suction side of the compressor 1 and the gas side of the outdoor heat exchanger 3.
- the refrigerant flow path is switched (solid line of the four-way valve 2 in FIG. 1).
- the indoor heat exchanger 7 functions as a condenser for the refrigerant compressed in the compressor 1
- the outdoor heat exchanger 3 is a refrigerant that is condensed in the indoor heat exchanger 7. It functions as an evaporator.
- the outdoor heat exchanger 3 is composed of a cross fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins.
- the outdoor heat exchanger 3 has a gas-side pipe connected to the four-way valve 2, a liquid-side pipe connected to the liquid connection pipe 6, functions as a refrigerant condenser during cooling operation, and a refrigerant evaporator during heating operation. Function as.
- the outdoor air blower 4 is a fan capable of changing the flow rate of air supplied to the outdoor heat exchanger 3, and is composed of, for example, a propeller fan driven by a DC motor (not shown).
- the outdoor blower 4 has a function of sucking outdoor air into the heat source unit A and discharging the air exchanged with the refrigerant in the outdoor heat exchanger 3 to the outside.
- the decompression device 5 is a device that is connected to the liquid side of the heat source unit A and adjusts the flow rate of the refrigerant flowing in the refrigerant circuit.
- the accumulator 11 is a refrigerant container that is connected to the suction side piping of the compressor 1.
- the accumulator 11 returns the refrigeration oil that has flowed out of the compressor 1 together with the refrigerant to the compressor 1 while suppressing the excessive inflow of liquid refrigerant to the compressor 1 and the function of storing surplus refrigerant during operation. It has a function to do.
- the bypass pipe 12 is a pipe having one end inserted into the accumulator 11 and the other end bypassed to the suction side pipe of the compressor 1.
- the flow rate adjusting valve 13 is provided in the flow path of the bypass pipe 12 and adjusts the flow rate of the refrigerant or the like flowing through the bypass pipe 12.
- the bypass pipe 12 on the inner side of the accumulator 11 does not include the oil return hole 14.
- the bypass pipe 12 on the inner side of the accumulator 11 may include a plurality of oil return holes 14 along the vertical direction.
- the compressor 1 is provided with a discharge temperature sensor 201 for detecting the refrigerant discharge temperature Td and a compressor shell temperature sensor 208 for detecting the compressor shell temperature. Further, a compressor suction pressure sensor 209 is provided in the suction side piping of the compressor 1, and a compressor discharge pressure sensor 210 is provided in the discharge side piping of the compressor 1.
- the outdoor heat exchanger 3 is provided with a gas side temperature sensor 202 that detects the temperature of the refrigerant in the gas-liquid two-phase state. As the temperature of the refrigerant in the gas-liquid two-phase state, there is a refrigerant temperature corresponding to the condensation temperature Tc during the cooling operation or the evaporation temperature Te during the heating operation. Furthermore, the liquid side pipe of the outdoor heat exchanger 3 is provided with a liquid side temperature sensor 204 that detects the temperature of the refrigerant in the liquid state or the gas-liquid two-phase state.
- an outdoor temperature sensor 203 for detecting the temperature of the outdoor air flowing into the unit, that is, the outdoor air temperature Ta, is provided on the outdoor air inlet side of the heat source unit A.
- the discharge temperature sensor 201, the gas side temperature sensor 202, the outdoor temperature sensor 203, the liquid side temperature sensor 204, and the compressor shell temperature sensor 208 are all formed of thermistors.
- operation of the compressor 1, the four-way valve 2, the outdoor air blower 4, and the decompression device 5 is controlled by the control apparatus 30 (operation control means).
- the heat source unit A and the utilization unit B are connected via the liquid connection pipe 6 and the gas connection pipe 9 to constitute the refrigerant circuit of the air conditioner 100.
- the configuration in the case where there is one heat source unit A will be described as an example.
- the present invention is not limited to this, and there may be a plurality of heat source units A that are two or more. Good.
- the respective capacities may be different or all may have the same capacity.
- a four-way valve 2 is provided to configure a refrigerant circuit capable of switching between heating operation and cooling operation, but the present invention is not limited to this.
- only the cooling operation or only the heating operation may be performed without providing the four-way valve 2.
- FIG. 3 is a control block diagram of the air-conditioning apparatus 100 according to the embodiment of the present invention. As shown in FIG. 3, the control device 30 performs measurement control of sensors and actuators.
- the control device 30 is built in the air conditioner 100, and includes a measurement unit 30a, a calculation unit 30b, a drive unit 30c, a storage unit 30d, and a determination unit 30e.
- the measurement unit 30a, the calculation unit 30b, the drive unit 30c, and the determination unit 30e are configured by, for example, a microcomputer.
- the storage unit 30d is configured by a semiconductor memory or the like.
- the measuring unit 30a receives operating state quantities detected from various sensors (pressure sensor and temperature sensor), and measures pressure and temperature.
- the operation state quantity measured by the measurement unit 30a is input to the calculation unit 30b.
- the “first detector” in the present invention is configured by the measurement unit 30a and various sensors.
- the calculation unit 30b calculates, for example, a refrigerant physical property value (saturation pressure, saturation temperature, enthalpy, etc.) based on the operation state quantity measured by the measurement unit 30a, using a formula given in advance.
- the computing unit 30b corresponds to the “second detector” in the present invention.
- the driving unit 30c drives the compressor 1, the outdoor blower 4, the decompressor 5, the flow rate adjusting valve 13, and the like based on the calculation result of the calculation unit 30b.
- the calculation unit 30b and the drive unit 30c constitute a “control unit” in the present invention.
- the storage unit 30d stores, as a result of the calculation unit 30b, a predetermined constant, a function expression for calculating a physical property value (saturation pressure, saturation temperature, dryness, etc.) of the refrigerant, a function table (table), and the like. To do. These stored contents in the storage unit 30d can be referred to and rewritten as necessary.
- a control program is further stored in the storage unit 30d, and the control device 30 controls the air conditioner 100 according to the program in the storage unit 30d.
- the determination unit 30e performs processing such as large / small comparison and determination based on the result obtained by the calculation unit 30b.
- the determination unit 30e corresponds to the “determination unit” in the present invention.
- the control device 30 is built in the air conditioner 100, but the present invention is not limited to this.
- the main control unit is provided in the heat source unit A, the sub-control unit having a part of the function of the control device 30 is provided in the use unit B, and the data communication is performed between the main control unit and the sub-control unit to perform the cooperation process.
- the four-way valve 2 is in the state indicated by the broken line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the gas side of the outdoor heat exchanger 3, and the suction side of the compressor 1 is the indoor heat exchanger 7 It is in the state connected to the gas side.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 reaches the outdoor heat exchanger 3 that is a condenser via the four-way valve 2, and the refrigerant is condensed and liquefied by the blowing action of the outdoor blower 4, and the high-pressure and low-temperature refrigerant. It becomes.
- the condensed and liquefied high-pressure and low-temperature refrigerant is decompressed by the decompression device 5 to become a two-phase refrigerant, is sent to the utilization unit B via the liquid connection pipe 6, and is sent to the indoor heat exchanger 7.
- the decompressed two-phase refrigerant evaporates by the blowing action of the indoor blower 8 in the indoor heat exchanger 7 that is an evaporator, and becomes a low-pressure gas refrigerant.
- the low-pressure gas refrigerant is sucked into the compressor 1 again via the four-way valve 2 and the accumulator 11.
- the decompression device 5 controls the flow rate of the refrigerant flowing through the indoor heat exchanger 7 by adjusting the opening degree so that the refrigerant supercooling degree at the outlet of the outdoor heat exchanger 3 becomes a predetermined value. For this reason, the liquid refrigerant condensed in the outdoor heat exchanger 3 has a predetermined degree of supercooling.
- the refrigerant subcooling degree at the outlet of the outdoor heat exchanger 3 is detected by a value obtained by subtracting the gas side temperature sensor 202 (equivalent to the refrigerant condensation temperature Tc) from the detection value of the liquid side temperature sensor 204.
- required in the air-conditioning space in which the utilization unit B was installed flows into the indoor heat exchanger 7.
- the heating operation will be described with reference to FIG.
- the four-way valve 2 is in the state indicated by the solid line in FIG. 1, that is, the discharge side of the compressor 1 is connected to the gas side of the indoor heat exchanger 7 and the suction side of the compressor 1 is the outdoor heat exchanger 3. It is in the state connected to the gas side.
- the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 is sent to the utilization unit B via the four-way valve 2 and the gas connection pipe 9. Then, the high-temperature and high-pressure gas refrigerant reaches the indoor heat exchanger 7 that is a condenser, and the refrigerant is condensed and liquefied by the blowing action of the indoor blower 8, and becomes a high-pressure and low-temperature refrigerant.
- the condensed and liquefied high-pressure and low-temperature refrigerant is sent to the heat source unit A via the liquid connection pipe 6, is decompressed by the decompression device 5, becomes a two-phase refrigerant, and is sent to the outdoor heat exchanger 3.
- the decompressed two-phase refrigerant evaporates in the outdoor heat exchanger 3 that is an evaporator by the blowing action of the outdoor blower 4, and becomes a low-pressure gas refrigerant.
- the low-pressure gas refrigerant is sucked into the compressor 1 again via the four-way valve 2 and the accumulator 11.
- the decompression device 5 controls the flow rate of the refrigerant flowing through the indoor heat exchanger 7 by adjusting the opening degree so that the refrigerant supercooling degree at the outlet of the indoor heat exchanger 7 becomes a predetermined value. For this reason, the liquid refrigerant condensed in the indoor heat exchanger 7 has a predetermined degree of supercooling.
- the refrigerant subcooling degree at the outlet of the indoor heat exchanger 7 is detected by a value obtained by subtracting the gas side temperature sensor 207 (equivalent to the refrigerant condensation temperature Tc) from the detection value of the liquid side temperature sensor 205.
- required in the air-conditioning space in which the utilization unit B was installed flows into the indoor heat exchanger 7.
- the detected value of the temperature sensor installed in each heat exchanger is used as the refrigerant condensing temperature Tc.
- the refrigerant discharge pressure is detected by the compressor discharge pressure sensor 210 of the compressor 1, and the discharge pressure The detected value may be converted into a saturation temperature and used as the refrigerant condensing temperature Tc.
- FIG. 4 is a flowchart showing a flow of control operation of the flow rate adjustment valve 13 of the air-conditioning apparatus 100 according to the embodiment of the present invention.
- the control operation of the flow rate adjusting valve 13 will be described with reference to FIG.
- the measurement unit 30a detects the refrigerant container temperature Tacc. Thereafter, the process proceeds to (STEP 12).
- the refrigerant container internal temperature Tacc is the refrigerant temperature in the accumulator 11, and for example, the refrigerant evaporation temperature Te is used.
- the detected value of the gas side temperature sensor 207 provided in the indoor heat exchanger 7 is used as the evaporation temperature Te of the refrigerant during the cooling operation.
- the detected value of the gas side temperature sensor 202 provided in the outdoor heat exchanger 3 is used for the evaporation temperature Te of the refrigerant during the heating operation.
- the detected value of the temperature sensor installed in each heat exchanger was used here as the evaporation temperature of the refrigerant.
- the suction pressure of the refrigerant may be detected by a compressor suction pressure sensor 209 provided on the suction side of the compressor 1, and the detected value of the suction pressure may be converted into a saturation temperature and used as the refrigerant evaporation temperature.
- a refrigerant temperature sensor may be installed in the inlet side piping of the accumulator 11, and the detected value of the temperature sensor may be used as the refrigerant container internal temperature Tacc.
- the determination unit 30e compares the two-layer separation temperature T0 of the refrigerating machine oil stored in the storage unit 30d in advance with the refrigerant container internal temperature Tacc, and the two-layer separation of the liquid refrigerant and the refrigerating machine oil is performed in the accumulator 11. Determine if it has occurred. If the refrigerant container internal temperature Tacc is lower than the two-layer separation temperature T0, it is determined that the two-layer separation of the liquid refrigerant and the refrigerating machine oil has occurred (STEP 13). On the other hand, if the refrigerant container internal temperature Tacc is higher than the two-layer separation temperature T0, it is determined that the two-layer separation has not occurred (YES in STEP 17).
- the calculation unit 30b calculates the refrigerant superheat degree SHs of the compressor 1. Thereafter, the process proceeds to (STEP 15).
- the intake refrigerant superheat degree SHs is a value obtained by subtracting the refrigerant evaporation temperature Te from the intake refrigerant temperature Ts of the compressor 1.
- the detected value of the gas side temperature sensor 207 provided in the indoor heat exchanger 7 is used as the evaporation temperature Te of the refrigerant during the cooling operation.
- the detected value of the gas side temperature sensor 202 provided in the outdoor heat exchanger 3 is used for the evaporation temperature Te of the refrigerant during the heating operation.
- the suction refrigerant temperature Ts is calculated by a low pressure Ps (equivalent to the suction pressure of the compressor 1) obtained by converting the refrigerant evaporation temperature Te into a saturation pressure and a high pressure Pd (compression) obtained by converting the refrigerant condensation temperature Tc into a saturation pressure. Equivalent to the discharge pressure of the machine 1).
- the compression process of the compressor 1 is assumed to be a polytropic change of the polytropic index n, and the refrigerant discharge temperature Td detected by the discharge temperature sensor 201 of the compressor 1 is used. It can be obtained from the following formula.
- Ts and Td are temperature [K]
- Ps and Pd are pressure [MPa]
- n is a polytropic index [ ⁇ ].
- the high pressure (discharge refrigerant pressure) Pd and the low pressure (intake refrigerant pressure) Ps of the refrigerant are calculated based on the condensation temperature Tc and the evaporation temperature Te of the refrigerant. It may be obtained using the compressor suction pressure sensor 209 on the suction side and the compressor discharge pressure sensor 210 on the discharge side. Further, a temperature sensor may be installed on the suction side of the compressor 1 to directly detect the suction refrigerant temperature Ts.
- Step 15 Based on the calculated suction refrigerant superheat degree SHs, it is determined whether or not the suction refrigerant of the compressor 1 is in a superheated gas state. If the intake refrigerant of the compressor 1 is in the superheated gas state (SHs> 0), the control flow is terminated as it is. If the suction refrigerant of the compressor 1 is not in the superheated gas state, the process proceeds to (STEP 16).
- the calculating part 30b adjusts the opening degree of the flow regulating valve 13 in the closing direction via the driving part 30c. Thereafter, the process proceeds to (STEP 14).
- the adjustment of the opening degree of the flow rate adjusting valve 13 is, for example, when an electronic expansion valve is used as the flow rate adjusting valve 13, the opening degree by a certain opening degree (for example, 20 pulses) according to the specification of the valve and the opening characteristic. Make adjustments using a method that reduces the size.
- an electronic expansion valve is used as an example of the flow rate adjusting valve 13, but other types of flow rate adjusting valves 13 may be used as long as the same opening degree adjustment is possible.
- the flow rate adjustment valve 13 is based on the suction refrigerant dryness instead of the suction refrigerant superheat degree SHs.
- the method of adjusting the opening degree of 13 may be sufficient.
- the degree of dryness of the suction refrigerant can be stored in advance in the storage unit 30d as the physical property information of the refrigerant, and can be obtained using the suction refrigerant temperature Ts of the compressor 1 or the low pressure (intake refrigerant pressure) Ps.
- the calculation unit 30b adjusts the opening degree of the flow rate adjustment valve 13 via the drive unit 30c based on the two-layer separation state and the suction refrigerant superheat degree SHs, so that the two-layer separation state with high accuracy is achieved.
- By-pass flow control by judgment was made possible. Thereby, avoidance of unnecessary liquid back and oil return to the compressor 1 are possible, and failure of the compressor 1 due to liquid back or seizure of the sliding portion of the compressor 1 can be avoided. High reliability can be realized.
- the calculation unit 30b adjusts the opening degree of the flow rate adjustment valve 13 provided in the bypass pipe 12 via the drive unit 30c based on the suction refrigerant state on the suction side of the compressor 1. By doing so, it is possible to always ensure an appropriate refrigerant flow rate and oil return amount to the compressor 1 regardless of the operation state of the refrigerant circuit and the operating conditions such as the outside air condition, resulting in performance degradation and deterioration in reliability. Can be prevented.
- a plurality of oil return holes 14 are provided at the tip of the pipe inserted into the inside of the accumulator 11.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Description
[機器構成]
図1は、本発明の実施の形態に係る空気調和装置100を概略的に示す冷媒回路の構成図である。空気調和装置100は、蒸気圧縮式の冷凍サイクル運転を行うことによって、屋内の冷暖房に使用される装置である。図1に示されるように、空気調和装置100は、熱源ユニットAと複数台の利用ユニットBとから構成されている。なお、本実施の形態では、1台の利用ユニットBの場合を例として説明する。熱源ユニットAと複数台の利用ユニットBとは、冷媒連絡配管となる液接続配管6及びガス接続配管9を介して接続されている。
利用ユニットBは、屋内の天井への埋め込み、吊り下げ、又は屋内の壁面に壁掛け等により設置されている。利用ユニットBは、上述したように液接続配管6及びガス接続配管9を介して熱源ユニットAに接続されて冷媒回路の一部を構成している。
次に、熱源ユニットAの詳細な構成について説明する。熱源ユニットAは、屋外に設置されており、液接続配管6及びガス接続配管9を介して利用ユニットBに接続されており、冷媒回路の一部を構成している。
続いて、本実施の形態の空気調和装置100の各運転モードにおける動作を説明する。まず、冷房運転の動作について図1を用いて説明する。
図4は、本発明の実施の形態に係る空気調和装置100の流量調整弁13の制御動作の流れを示すフローチャートである。以下、図1を参照しながら図4の各ステップに基づいて、流量調整弁13の制御動作について説明する。
フロー開始後、測定部30aは、冷媒容器内温度Taccを検出する。その後、(STEP12)へ移行する。ここで、冷媒容器内温度Taccはアキュムレータ11内の冷媒温度であり、例えば冷媒の蒸発温度Teを用いる。冷房運転時における冷媒の蒸発温度Teは、室内熱交換器7に設けられたガス側温度センサ207の検出値を用いる。また、暖房運転時における冷媒の蒸発温度Teは、室外熱交換器3に設けられたガス側温度センサ202の検出値を用いる。
判定部30eは、あらかじめ記憶部30dに記憶しておいた冷凍機油の二層分離温度T0と、冷媒容器内温度Taccとを比較して、アキュムレータ11内において液冷媒と冷凍機油の二層分離が生じているかどうか判定する。冷媒容器内温度Taccが、二層分離温度T0よりも低ければ、液冷媒と冷凍機油の二層分離が生じていると判断し(STEP13)へ移行する。一方、冷媒容器内温度Taccが、二層分離温度T0よりも高ければ、二層分離が生じていないと判断し(STEP17)へ移行する。
演算部30bは、駆動部30cを介して流量調整弁13を全開とする。その後、(STEP14)へ移行する。
演算部30bは、圧縮機1の吸入冷媒過熱度SHsを算出する。その後、(STEP15)へ移行する。ここで、吸入冷媒過熱度SHsは、圧縮機1の吸入冷媒温度Tsから冷媒の蒸発温度Teを引いた値である。冷房運転時における冷媒の蒸発温度Teは、室内熱交換器7に設けられたガス側温度センサ207の検出値を用いる。また、暖房運転時における冷媒の蒸発温度Teは、室外熱交換器3に設けられたガス側温度センサ202の検出値を用いる。
算出した吸入冷媒過熱度SHsを基に圧縮機1の吸入冷媒が、過熱ガス状態かどうか判定する。圧縮機1の吸入冷媒が、過熱ガス状態(SHs>0)であれば、そのまま制御フローを終了する。圧縮機1の吸入冷媒が、過熱ガス状態でなければ、(STEP16)へ移行する。
演算部30bは、駆動部30cを介して流量調整弁13の開度を閉じる方向へ調整する。その後、(STEP14)へ移行する。ここで、流量調整弁13の開度調整は、例えば流量調整弁13として電子膨張弁を用いた場合、弁の仕様、及び開度特性に合わせて、一定開度(例えば20パルス)ずつ開度を小さくする方法で調整する。なお、ここでは流量調整弁13の例として電子膨張弁としたが、同様の開度調整が可能なものであれば他の方式の流量調整弁13を用いてもよい。
演算部30bは、駆動部30cを介して流量調整弁13を全閉にする。その後、制御フローを終了する。
本発明の特徴事項を各実施の形態において説明したが、例えば、冷媒の流路構成(配管接続)、圧縮機1、熱交換器、膨張弁等の冷媒回路要素の構成等の内容は、各実施の形態で説明した内容に限定されるものではなく、本発明の技術の範囲内で適宜変更が可能である。
Claims (5)
- 圧縮機、熱源側熱交換器、減圧装置、利用側熱交換器及び冷媒容器が順次配管を介して接続された冷媒回路と、
前記冷媒容器の内部に一端が挿入され、他端が前記圧縮機の吸引側の配管に接続されたバイパス配管と、
前記バイパス配管に設けられた流量調整弁と、
前記冷媒容器内の冷媒温度を検出する第一検出器と、
冷媒と冷凍機油の二層分離温度の情報を記憶する記憶部と、
前記冷媒温度と前記二層分離温度を比較して前記冷媒と前記冷凍機油の二層分離状態を判定する判定器と、
前記圧縮機の吸入冷媒状態を検出する第二検出器と、
前記二層分離状態及び前記吸入冷媒状態に基づいて前記流量調整弁の開度を調整する制御部と、を備えた
空気調和装置。 - 前記制御部は、前記判定器が前記冷媒と前記冷凍機油とが前記二層分離状態でないと判定した場合には、前記流量調整弁の開度を全閉とし、前記判定器が前記冷媒と前記冷凍機油とが前記二層分離状態であると判定した場合には、前記流量調整弁の開度を全開とする
請求項1に記載の空気調和装置。 - 前記第二検出器は、吸入冷媒過熱度を検出し、
前記制御部は、前記流量調整弁が全開となった後、前記吸入冷媒過熱度に基づいて、前記圧縮機に吸入される前記冷媒が常に過熱ガス状態となるように、前記流量調整弁の開度を調整する
請求項2に記載の空気調和装置。 - 前記第二検出器は、前記圧縮機に吸入される前記冷媒の吸入冷媒乾き度を検出し、
前記制御部は、前記流量調整弁が全開となった後、前記吸入冷媒乾き度に基づいて、前記圧縮機に吸入される前記冷媒が常に飽和ガス状態もしくは過熱ガス状態となるように、前記流量調整弁の開度を調整する
請求項2に記載の空気調和装置。 - 前記バイパス配管は、前記冷媒容器の内部に挿入された部分に、上下方向に沿って複数の油戻し穴を備える
請求項1~4のいずれか一項に記載の空気調和装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201580073268.0A CN107208937A (zh) | 2015-01-23 | 2015-01-23 | 空气调节装置 |
EP15866389.8A EP3088819B1 (en) | 2015-01-23 | 2015-01-23 | Air conditioning device |
US15/524,024 US10753660B2 (en) | 2015-01-23 | 2015-01-23 | Air-conditioning apparatus |
PCT/JP2015/051919 WO2016117128A1 (ja) | 2015-01-23 | 2015-01-23 | 空気調和装置 |
JP2016570463A JP6366742B2 (ja) | 2015-01-23 | 2015-01-23 | 空気調和装置 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2015/051919 WO2016117128A1 (ja) | 2015-01-23 | 2015-01-23 | 空気調和装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016117128A1 true WO2016117128A1 (ja) | 2016-07-28 |
Family
ID=56416693
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2015/051919 WO2016117128A1 (ja) | 2015-01-23 | 2015-01-23 | 空気調和装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US10753660B2 (ja) |
EP (1) | EP3088819B1 (ja) |
JP (1) | JP6366742B2 (ja) |
CN (1) | CN107208937A (ja) |
WO (1) | WO2016117128A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107436060A (zh) * | 2017-07-04 | 2017-12-05 | 广东美的制冷设备有限公司 | 空调器以及空调器的回液检测装置和方法 |
JP2019032133A (ja) * | 2017-08-09 | 2019-02-28 | シャープ株式会社 | 空調機 |
US20190178543A1 (en) * | 2017-12-12 | 2019-06-13 | Rheem Manufacturing Company | Accumulator and Oil Separator |
WO2023248706A1 (ja) * | 2022-06-20 | 2023-12-28 | サンデン株式会社 | 車両用空調装置 |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10451324B2 (en) * | 2014-05-30 | 2019-10-22 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
JP6323489B2 (ja) * | 2015-08-04 | 2018-05-16 | 株式会社デンソー | ヒートポンプシステム |
CN106524336B (zh) * | 2016-11-07 | 2019-04-30 | 广东美的暖通设备有限公司 | 多联机系统及其防回液控制方法 |
WO2019106795A1 (ja) * | 2017-11-30 | 2019-06-06 | 三菱電機株式会社 | 冷凍サイクル装置 |
CN108180679B (zh) * | 2017-12-27 | 2020-12-18 | 青岛海信日立空调系统有限公司 | 制冷系统、空调器以及空调器的控制方法 |
JP2020104591A (ja) * | 2018-12-26 | 2020-07-09 | 株式会社ヴァレオジャパン | 車両用空調装置 |
CN110145900A (zh) * | 2019-04-28 | 2019-08-20 | 北京君腾达制冷技术有限公司 | 一种空调及其防止压缩机液击装置和方法 |
JP6828790B1 (ja) * | 2019-10-31 | 2021-02-10 | ダイキン工業株式会社 | 冷凍装置 |
US11407274B2 (en) | 2020-03-12 | 2022-08-09 | Denso International America, Inc | Accumulator pressure drop regulation system for a heat pump |
CN111795474B (zh) * | 2020-07-17 | 2021-11-23 | 广东Tcl智能暖通设备有限公司 | 空调器的控制方法、控制装置、空调器及存储介质 |
CN113587253B (zh) * | 2021-07-05 | 2023-03-21 | 青岛海信日立空调系统有限公司 | 一种空调器 |
EP4368920A1 (en) * | 2021-07-07 | 2024-05-15 | Mitsubishi Electric Corporation | Accumulator and refrigeration cycle device |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006078087A (ja) * | 2004-09-09 | 2006-03-23 | Daikin Ind Ltd | 冷凍装置 |
JP2011163671A (ja) | 2010-02-10 | 2011-08-25 | Mitsubishi Electric Corp | 受液器及びそれを用いた冷凍サイクル装置 |
JP2012082993A (ja) * | 2010-10-07 | 2012-04-26 | Yanmar Co Ltd | エンジン駆動式空調機 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3104513B2 (ja) * | 1993-12-28 | 2000-10-30 | 三菱電機株式会社 | アキュムレータ |
JP3339302B2 (ja) * | 1996-04-26 | 2002-10-28 | 三菱電機株式会社 | アキュムレータ |
JPH10160293A (ja) * | 1996-11-29 | 1998-06-19 | Sanyo Electric Co Ltd | 冷凍装置及びアキュームレータ |
DE10062948C2 (de) * | 2000-12-16 | 2002-11-14 | Eaton Fluid Power Gmbh | Kältemaschine mit kontrollierter Kältemittelphase vor dem Verdichter |
JP3743861B2 (ja) * | 2002-03-06 | 2006-02-08 | 三菱電機株式会社 | 冷凍空調装置 |
DE10344588A1 (de) * | 2003-09-25 | 2005-05-12 | Bosch Gmbh Robert | Klimaanlage und Verfahren zum Betreiben einer Klimaanlage |
CN102066851B (zh) * | 2008-06-13 | 2013-03-27 | 三菱电机株式会社 | 冷冻循环装置及其控制方法 |
JP2012007864A (ja) * | 2010-06-28 | 2012-01-12 | Mitsubishi Electric Corp | 受液器及びそれを用いた冷凍サイクル装置 |
EP2863148B1 (en) * | 2012-04-27 | 2021-03-17 | Mitsubishi Electric Corporation | Air conditioning device |
-
2015
- 2015-01-23 CN CN201580073268.0A patent/CN107208937A/zh active Pending
- 2015-01-23 WO PCT/JP2015/051919 patent/WO2016117128A1/ja active Application Filing
- 2015-01-23 JP JP2016570463A patent/JP6366742B2/ja active Active
- 2015-01-23 US US15/524,024 patent/US10753660B2/en active Active
- 2015-01-23 EP EP15866389.8A patent/EP3088819B1/en active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006078087A (ja) * | 2004-09-09 | 2006-03-23 | Daikin Ind Ltd | 冷凍装置 |
JP2011163671A (ja) | 2010-02-10 | 2011-08-25 | Mitsubishi Electric Corp | 受液器及びそれを用いた冷凍サイクル装置 |
JP2012082993A (ja) * | 2010-10-07 | 2012-04-26 | Yanmar Co Ltd | エンジン駆動式空調機 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3088819A4 |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107436060A (zh) * | 2017-07-04 | 2017-12-05 | 广东美的制冷设备有限公司 | 空调器以及空调器的回液检测装置和方法 |
CN107436060B (zh) * | 2017-07-04 | 2020-01-14 | 广东美的制冷设备有限公司 | 空调器以及空调器的回液检测装置和方法 |
JP2019032133A (ja) * | 2017-08-09 | 2019-02-28 | シャープ株式会社 | 空調機 |
US20190178543A1 (en) * | 2017-12-12 | 2019-06-13 | Rheem Manufacturing Company | Accumulator and Oil Separator |
US10845106B2 (en) * | 2017-12-12 | 2020-11-24 | Rheem Manufacturing Company | Accumulator and oil separator |
WO2023248706A1 (ja) * | 2022-06-20 | 2023-12-28 | サンデン株式会社 | 車両用空調装置 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2016117128A1 (ja) | 2017-07-27 |
EP3088819B1 (en) | 2021-09-15 |
US10753660B2 (en) | 2020-08-25 |
JP6366742B2 (ja) | 2018-08-01 |
EP3088819A1 (en) | 2016-11-02 |
EP3088819A4 (en) | 2016-12-21 |
US20170336116A1 (en) | 2017-11-23 |
CN107208937A (zh) | 2017-09-26 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP6366742B2 (ja) | 空気調和装置 | |
JP4864110B2 (ja) | 冷凍空調装置 | |
JP5334909B2 (ja) | 冷凍空調装置並びに冷凍空調システム | |
JP7186845B2 (ja) | 空気調和装置 | |
WO2015004747A1 (ja) | 冷凍サイクル装置 | |
JP5094801B2 (ja) | 冷凍サイクル装置及び空気調和装置 | |
US20140345310A1 (en) | Refrigeration cycle apparatus | |
WO2010061643A1 (ja) | 冷凍サイクル装置 | |
JP6730532B2 (ja) | 冷凍サイクル装置および冷凍装置 | |
US20170167762A1 (en) | Refrigeration cycle apparatus | |
AU2006324593A1 (en) | Air conditioner | |
JP5744081B2 (ja) | 空気調和装置 | |
CN112840164B (zh) | 空调装置和管理装置 | |
JP2011012958A (ja) | 冷凍サイクル装置の制御方法 | |
JP6732862B2 (ja) | 冷凍装置 | |
WO2017179210A1 (ja) | 冷凍装置 | |
JP6537629B2 (ja) | 空気調和装置 | |
JP6410935B2 (ja) | 空気調和機 | |
JP6449979B2 (ja) | 冷凍装置 | |
JP6112189B1 (ja) | 空気調和装置 | |
JP6779361B2 (ja) | 空気調和装置 | |
JP2008111584A (ja) | 空気調和装置 | |
JP5858022B2 (ja) | 空気調和装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
REEP | Request for entry into the european phase |
Ref document number: 2015866389 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2015866389 Country of ref document: EP |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 15866389 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2016570463 Country of ref document: JP Kind code of ref document: A |
|
NENP | Non-entry into the national phase |
Ref country code: DE |