WO2007111303A1 - 冷凍装置 - Google Patents
冷凍装置 Download PDFInfo
- Publication number
- WO2007111303A1 WO2007111303A1 PCT/JP2007/056221 JP2007056221W WO2007111303A1 WO 2007111303 A1 WO2007111303 A1 WO 2007111303A1 JP 2007056221 W JP2007056221 W JP 2007056221W WO 2007111303 A1 WO2007111303 A1 WO 2007111303A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pressure
- refrigerant
- heat exchanger
- temperature
- throttle
- Prior art date
Links
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
- 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- 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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
-
- 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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- 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
- F25B2313/005—Outdoor unit expansion 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
- 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
-
- 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
- F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way 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
- 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
-
- 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
- F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way 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
- 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
-
- 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
-
- 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
- F25B2400/13—Economisers
-
- 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
-
- 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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
Definitions
- the present invention relates to a refrigeration apparatus, and particularly relates to measures for operating efficiency in a refrigeration apparatus of a supercritical refrigeration cycle.
- some refrigeration apparatuses include a refrigerant circuit that performs a vapor compression refrigeration cycle using carbon dioxide as a refrigerant and using a supercritical cycle (see Patent Document 1).
- This refrigeration apparatus includes a refrigerant circuit in which a low-stage compressor, a high-stage compressor, a heat-dissipation-side heat exchanger, a first decompressor, a gas-liquid separator, and a second decompressor are connected in order.
- the gas refrigerant of the gas-liquid separator is guided between the low-stage compressor and the high-stage compressor.
- the refrigeration apparatus uses a supercritical cycle, the refrigerant becomes supercritical in the heat-dissipation side heat exchanger, and there is no condensation temperature. Therefore, the amount of decompression of at least one of the first decompressor and the second decompressor is controlled based on the outlet refrigerant temperature of the heat dissipation side heat exchanger or the ambient air temperature of the heat dissipation side heat exchanger, and the refrigerant circuit Control is performed to optimize the high-pressure refrigerant pressure.
- Patent Document 1 Japanese Patent Laid-Open No. 2001-133058
- the high-pressure refrigerant pressure in the refrigerant circuit changes with this change when both the outlet refrigerant temperature of the heat radiation side heat exchanger and the ambient air temperature of the heat radiation side heat exchanger change. Therefore, the operating efficiency (COP) of the refrigeration system varies depending on the high-pressure refrigerant pressure in the refrigerant circuit, the outlet refrigerant temperature of the heat-dissipating side heat exchanger, and the ambient air temperature of the heat-dissipating side heat exchanger.
- the conventional refrigeration apparatus adjusts the amount of pressure reduction based on the high-pressure refrigerant pressure of the refrigerant circuit and the outlet refrigerant temperature of the heat-dissipation side heat exchanger, or the high-pressure refrigerant pressure of the refrigerant circuit and the heat-dissipation side heat exchange.
- the amount of decompression is adjusted based on the ambient air temperature of the vessel.
- the conventional refrigeration equipment cannot always be said to perform the optimum operation with the operation efficiency (COP).
- the present invention has been made in view of such a point, and performs an optimum operation of operating efficiency (COP) in comparison with a refrigeration apparatus having a refrigerant circuit of a supercritical refrigeration cycle. With the goal.
- COP operating efficiency
- the first invention includes a compression mechanism (30), a heat source side heat exchanger (21), an expansion mechanism (40), and a use side heat exchanger (23), and a vapor compression supercritical refrigeration cycle.
- a high-pressure side throttle mechanism (41, 42) having a variable throttle amount and a low-pressure side throttle so that the expansion mechanism (40) expands the refrigerant of the refrigerant circuit (20) in two stages.
- the target is a refrigeration system equipped with a mechanism (42, 41).
- the outlet refrigerant temperature of the heat release side heat exchanger as a radiator, and the refrigerant in the heat release side heat exchanger A target value for the high pressure refrigerant pressure of the refrigerant circuit (20) is derived based on the inlet medium temperature of the heat release side heat exchanger for the heat exchange medium, and the expansion mechanism so that the high pressure refrigerant pressure becomes the target value.
- High pressure control means (61) for adjusting the throttle amount of (40) and performing high pressure control is provided.
- the relationship between the high-pressure refrigerant pressure of the refrigerant circuit (20) and the outlet refrigerant temperature of the heat radiation side heat exchanger is determined by the inlet medium temperature of the heat radiation side heat exchanger.
- the target value of the high-pressure refrigerant pressure of the refrigerant circuit (20), which is the optimal COP, is derived from the inlet medium temperature of the heat exchanger and the outlet refrigerant temperature of the heat dissipation side heat exchanger. Then, the throttle amount of the expansion mechanism (40) is adjusted so that the high-pressure refrigerant pressure becomes the target value.
- the second invention includes a compression mechanism (30), a heat source side heat exchanger (21), an expansion mechanism (40), and a use side heat exchanger (23), and a vapor compression supercritical refrigeration cycle.
- the expansion mechanism (40) includes a high-pressure side throttle mechanism (42) and a low-pressure side throttle mechanism (42) having a variable throttle amount so as to expand the refrigerant in the refrigerant circuit (20) in two stages. 41) The
- a target value of the outlet refrigerant temperature of the use side heat exchanger (23) is derived based on the set pressure value of the high pressure refrigerant pressure, and the expansion mechanism (40 ) Is provided with outlet temperature control means (63) for controlling the outlet temperature by adjusting the throttle amount.
- the relationship between the high-pressure refrigerant pressure of the refrigerant circuit (20) and the outlet refrigerant temperature of the use side heat exchanger (23) is determined by the inlet medium temperature of the use side heat exchanger (23). Therefore, the target value of the outlet refrigerant temperature of the use side heat exchanger (23) that is the optimum COP is derived from the set value of the high pressure refrigerant pressure and the inlet medium temperature of the use side heat exchanger (23). Then, the throttle amount of the expansion mechanism (40) is adjusted so that the outlet refrigerant temperature becomes the target value.
- the third invention includes a compression mechanism (30), a heat source side heat exchanger (21), and an expansion mechanism (40), and a plurality of usage side heat exchangers (23) connected in parallel to each other.
- the refrigerant circuit (20) for performing the vapor compression supercritical refrigeration cycle is provided, and the expansion mechanism (40) is configured to expand the refrigerant in the refrigerant circuit (20) in two stages so that the heat source side heat exchanger (21 )
- a target value of the high-pressure refrigerant pressure of the refrigerant circuit (20) is derived, and the throttle amount of the expansion mechanism (40) is adjusted so that the high-pressure refrigerant pressure becomes the target value.
- High pressure control means (61) for adjusting the pressure to perform high pressure control is provided.
- a target value of the outlet refrigerant temperature of the use side heat exchanger (23) is derived based on the set pressure value of the high pressure refrigerant pressure, and the expansion mechanism (40 ) Is provided with outlet temperature control means (63) for controlling the outlet temperature by adjusting the throttle amount.
- the high-pressure refrigerant pressure of the refrigerant circuit (20) and the outlet of the heat radiation side heat exchanger Since the relationship with the refrigerant temperature is determined by the inlet medium temperature of the heat release side heat exchanger, during cooling operation, the inlet medium temperature of the heat source side heat exchanger (21) and the outlet refrigerant temperature of the heat source side heat exchanger (21)
- the target value of the high-pressure refrigerant pressure of the refrigerant circuit (20) with the optimum COP is derived.
- the throttle amount of the expansion mechanism (40) is adjusted so that the high-pressure refrigerant pressure becomes the target value.
- the target value of the outlet refrigerant temperature of the use side heat exchanger (23), which is the optimum COP, depending on the set value of the high pressure refrigerant pressure and the inlet medium temperature of the use side heat exchanger (23). is derived. Then, the throttle amount of the expansion mechanism (40) is adjusted so that the outlet refrigerant temperature becomes the target value.
- a fourth invention is the first control unit according to the first invention, wherein the high-pressure control means (61) adjusts a throttle amount of the high-pressure side throttle mechanism (41, 42) in order to perform high-pressure control. (6a), the heat source side heat exchanger (21), and the use side heat exchanger (23), the low pressure side throttle so that the degree of superheat of the outlet refrigerant of the heat absorption side heat exchanger as the heat absorber becomes a predetermined value. And a second control unit (6b) for adjusting the amount of aperture of the mechanism (42, 41).
- the first control unit (6a) performs high pressure control by adjusting the throttle amount of the high pressure side throttle mechanism (41, 42), and the second control unit (6b) performs low pressure side throttle.
- the degree of superheat is controlled by adjusting the throttle amount of the mechanism (42, 41).
- a fifth invention is the first control unit according to the second invention, wherein the outlet temperature control means (63) adjusts a throttle amount of the high pressure side throttle mechanism (42) in order to perform outlet temperature control. (6c) and a second control unit (6d) that adjusts the throttle amount of the low pressure side throttle mechanism (41) so that the degree of superheat of the outlet refrigerant of the heat source side heat exchanger (21) becomes a predetermined value. I'm going.
- the first control unit (6c) adjusts the throttle amount of the high pressure side throttle mechanism (42) to perform outlet temperature control, and the second control unit (6c) controls the low pressure side throttle mechanism. Adjust the throttle amount in (41) to control the superheat.
- a sixth invention is the first control unit (6a) according to the third invention, wherein the high-pressure control means (61) adjusts a throttle amount of the heat source side throttle mechanism (41) in order to perform high-pressure control. ) And a second control unit (6b) that adjusts the throttle amount of the usage-side throttle mechanism (42) so that the degree of superheat of the outlet refrigerant of the usage-side heat exchanger (23) becomes a predetermined value.
- the outlet temperature control means (63) adjusts the throttle amount of the use side throttle mechanism (42) to perform outlet temperature control.
- the first control section (6a) of the high pressure control means (61) includes the heat source side throttle mechanism (4
- the second control unit (6b) controls the degree of superheat by adjusting the throttle amount of the use side throttle mechanism (42) by adjusting the throttle amount of 1) and performing high pressure control.
- the first control unit (6c) of the outlet temperature control means (63) adjusts the throttle amount of the use side throttle mechanism (42) to perform outlet temperature control, and the second control unit (6c) The degree of superheat is controlled by adjusting the throttle amount of the side throttle mechanism (41).
- a seventh invention is the refrigerant circuit according to any one of the first to third inventions, wherein the refrigerant circuit (2
- the liquid refrigerant and the gas refrigerant are separated by the gas-liquid separator (22), and the gas refrigerant passes through the injection passage (25), and the intermediate pressure region of the compression mechanism (30). Will be introduced.
- the compression mechanism (30) includes a low stage compressor (33) and a high stage compressor (34), while the injection passage ( 25) is configured to guide the gas refrigerant to an intermediate pressure region between the low-stage compressor (33) and the high-stage compressor (34).
- the refrigerant is compressed in two stages by the low-stage compressor (33) and the high-stage compressor (34), and a gas-liquid separator is provided in the intermediate pressure region of the two-stage compression. Guide the gas refrigerant of (22).
- the high-pressure control means (61) is configured such that the outlet refrigerant temperature of the heat radiation side heat exchanger and the inlet medium temperature of the heat radiation side heat exchanger are on the heat source side.
- the refrigerant temperature equivalent saturation pressure in the heat absorption side heat exchanger as the heat absorber is added, and the outlet refrigerant temperature, the inlet medium temperature, the refrigerant temperature equivalent saturation pressure, and
- the target value for the high-pressure refrigerant pressure of the refrigerant circuit (20) is derived based on the above.
- the outlet refrigerant temperature of the heat radiation side heat exchanger and the heat input side of the heat radiation side heat exchanger is derived more accurately based on the inlet medium temperature and the saturation pressure corresponding to the refrigerant temperature in the heat absorption side heat exchanger.
- the high-pressure control means (61) force heat source side heat exchanger (21) outlet refrigerant temperature and heat source side heat exchanger (21) inlet medium temperature.
- a refrigerant temperature equivalent saturation pressure in the use side heat exchanger (23) is added, and the high pressure refrigerant pressure in the refrigerant circuit (20) is calculated based on the outlet refrigerant temperature, the inlet medium temperature, and the refrigerant temperature equivalent saturation pressure. The characteristic value is derived.
- the target value of the high-pressure refrigerant pressure of the refrigerant circuit (20) is derived more accurately.
- the capacity-up signal and the capacity-down signal output from the use-side unit (1B) in which the use-side heat exchanger (23) is housed Based on this, capacity control means (62) for increasing / decreasing the operating capacity of the compression mechanism (30) is provided.
- the capacity control means (62) separately controls increase / decrease of the operating capacity of the compression mechanism (30).
- the use side unit (1B) causes the use-side heat exchanger (23) to increase the capacity increase signal and the capacity limit based on the inlet medium temperature and the set temperature. It is configured to output a dumb signal.
- the operating capacity of the compression mechanism (30) is controlled to increase or decrease based on the inlet medium temperature and the set temperature of the use side heat exchanger (23).
- the operation capacity of the compression mechanism (30) is controlled so that the low pressure refrigerant pressure of the refrigerant circuit (20) becomes a set pressure value during the cooling operation.
- Capacity control means (62) is provided for controlling the operating capacity of the compression mechanism (30) so that the high-pressure refrigerant pressure of the refrigerant circuit (20) becomes a set pressure value during the thermal operation.
- the capacity control means (62) separately controls the operating capacity of the compression mechanism (30) so that the refrigerant pressure in the refrigerant circuit (20) becomes a set pressure value.
- the capacity control means (62) outputs a capacity increase signal output from the utilization side unit (1B) in which the utilization side heat exchanger (23) is accommodated.
- Base The low pressure refrigerant pressure setting value during cooling operation is reduced and the high pressure refrigerant pressure setting value during heating operation is increased, while the use side unit (1B) outputs the capacity down signal.
- the set pressure value of the low-pressure refrigerant pressure during the cooling operation is increased, and the set pressure value of the high-pressure refrigerant pressure during the heating operation is decreased.
- the operating capacity of the compression mechanism (30) is increased or decreased based on the capacity increase signal and the capacity decrease signal of the usage side unit (1B).
- the use side throttle mechanism (42) is constituted by an expansion valve having a variable opening
- the use side unit (1B) includes a use side throttle mechanism (When the opening of 42) becomes larger than a predetermined change value, a capacity up signal is output, and when the opening of the use side throttle mechanism (42) becomes smaller than the change value, a capacity down signal is output.
- the use side unit (1B) outputs a capacity increase signal when the opening degree of the use side throttle mechanism (42) is 80 to 90% or more of the full opening degree. It is configured to output a capacity down signal when the opening of the use-side throttle mechanism (42) falls below 10-20% of the full opening.
- the operating capacity of the compressor mechanism (30) is controlled to increase or decrease based on the opening degree of the use side throttle mechanism (42).
- the capacity control means (62) sets the set pressure value when the number of use side units (1B) that output the capacity up signal reaches a predetermined ratio.
- the set pressure value is changed when the number of usage-side units (1B) that output the capacity down signal reaches a predetermined ratio.
- the capacity control means (62) sets the predetermined ratio of the number of use side units (1B) for changing the set pressure value to 20 to 40%. It has been done.
- the target value of the high-pressure refrigerant pressure is derived from the inlet medium temperature of the heat-dissipation side heat exchanger and the outlet refrigerant temperature of the heat-dissipation side heat exchanger, and the high-pressure refrigerant Since the throttle amount of the expansion mechanism (40) is adjusted so that the pressure becomes the target value, the operation efficiency (COP) can be operated in an optimum operating state.
- OP can be operated in an optimal operating state.
- one of the throttle mechanisms (41, 42) performs high-pressure control, and the other throttle mechanism ((42, 41) performs superheat degree control.
- the high-pressure refrigerant and the low-pressure refrigerant can be kept in an optimum state.
- the outlet temperature control is performed by one of the throttle mechanisms (42) and the superheat degree control is performed by the other throttle mechanism (41) during the heating operation.
- the high-pressure refrigerant and the low-pressure refrigerant can be kept in optimum states.
- the high-pressure refrigerant of the gas-liquid separator (22) is guided to the intermediate pressure region of the compression mechanism (30) by the indication passage (25), the high-pressure refrigerant The pressure can be adjusted reliably.
- the ninth aspect of the present invention based on the outlet refrigerant temperature of the heat radiation side heat exchanger, the inlet medium temperature of the heat radiation side heat exchanger, and the saturation pressure corresponding to the refrigerant temperature of the heat absorption side heat exchanger. Since the target value of the high-pressure refrigerant pressure is derived, the target value of the high-pressure refrigerant pressure can be derived more accurately.
- FIG. 1 is a refrigerant circuit diagram showing a configuration of a refrigeration apparatus according to Embodiment 1.
- FIG. 2 is a control flow diagram showing throttle amount control of the throttle mechanism and capacity control of the compression mechanism during the cooling operation of the first embodiment.
- FIG. 3 is a control flow diagram showing throttle amount control of the throttle mechanism and capacity control of the compression mechanism during the heating operation of the first embodiment.
- FIG. 4 is a characteristic diagram showing the relationship between the high-pressure refrigerant pressure for each cooling capacity and the outlet refrigerant temperature when the outside air temperature is 30 ° C.
- Fig. 5 is a characteristic diagram showing the relationship between the high-pressure refrigerant pressure for each cooling capacity and the outlet refrigerant temperature when the outside air temperature is 35 ° C.
- Fig. 6 is a characteristic diagram showing the relationship between high-pressure refrigerant pressure and COP for each cooling capacity when the outside air temperature is 30 ° C.
- Fig. 7 is a characteristic diagram showing the relationship between high-pressure refrigerant pressure and COP for each cooling capacity when the outside air temperature is 35 ° C.
- Fig. 8 is a characteristic diagram showing the relationship between the outlet refrigerant temperature and the COP for each cooling capacity when the outside air temperature is 30 ° C.
- Fig. 9 is a characteristic diagram showing the relationship between outlet refrigerant temperature and COP for each cooling capacity when the outside air temperature is 35 ° C.
- FIG. 10 is a refrigerant circuit diagram showing the configuration of the refrigeration apparatus of Embodiment 2.
- FIG. 11 is a refrigerant circuit diagram showing the configuration of the refrigeration apparatus of Embodiment 3.
- FIG. 13 is a refrigerant circuit diagram showing the configuration of the refrigeration apparatus of the fourth embodiment.
- FIG. 13 is a control flowchart showing the throttle amount control of the throttle mechanism and the capacity control of the compression mechanism during the cooling operation of the fourth embodiment.
- FIG. 14 is a control flow diagram showing throttle amount control of the throttle mechanism and capacity control of the compression mechanism during heating operation of the fourth embodiment.
- FIG. 15 is a refrigerant circuit diagram showing the configuration of the refrigeration apparatus of the fifth embodiment.
- FIG. 16 is a refrigerant circuit diagram showing the configuration of the refrigeration apparatus of Embodiment 6.
- the refrigeration apparatus of the present embodiment is configured as an air conditioner (10) that switches between a cooling operation that is a cooling operation and a heating operation that is a heating operation.
- the air conditioner (10) includes a refrigerant circuit (20), and is configured as a so-called pair type air conditioner in which one indoor unit (1B) is connected to the outdoor unit (1A).
- the refrigerant circuit (20) includes a first throttle mechanism (41) that is one of a compression mechanism (30), a four-way switching valve (2a), an outdoor heat exchanger (21), and an expansion mechanism (40).
- the gas-liquid separator (22), the second throttle mechanism (42), which is one of the expansion mechanisms (40), and the indoor heat exchanger (23) are connected by a refrigerant pipe (24) to form a closed circuit.
- the refrigerant circuit (20) is configured to perform a vapor compression supercritical refrigeration cycle (a refrigeration cycle including a vapor pressure region higher than the critical temperature) filled with, for example, carbon dioxide (C02) as a refrigerant.
- a vapor compression supercritical refrigeration cycle a refrigeration cycle including a vapor pressure region higher than the critical temperature
- the outdoor unit (1A) includes a compression mechanism (30), a four-way switching valve (2a), an outdoor heat exchanger (21), a first throttle mechanism (41), a gas-liquid separator (22), 2
- the throttle mechanism (42) is housed in the heat source side unit. Make up.
- the indoor unit (1B) includes a indoor heat exchanger (23) and constitutes a use side unit.
- the compression mechanism (30) is configured such that an electric motor (31) and one compressor (32) connected to the electric motor (31) are housed in a vertically long cylindrical casing. Les.
- the compressor (32) is composed of a rotary piston type rotary compressor, for example.
- the outdoor heat exchanger (21) constitutes a heat source side heat exchanger that exchanges heat between the refrigerant and the outdoor air, while the indoor heat exchanger (23) exchanges heat between the refrigerant and the indoor air.
- the use side heat exchanger is configured.
- the outdoor heat exchanger (21) constitutes a heat radiation side heat exchanger that functions as a heat radiator that radiates the refrigerant discharged from the compression mechanism (30) to the outdoor air
- the indoor heat exchanger (23) constitutes an endothermic heat exchanger that functions as a heat absorber that absorbs heat from indoor air by evaporating the refrigerant decompressed by the expansion mechanism (40).
- the indoor heat exchanger (23) constitutes a heat radiation side heat exchanger that functions as a heat radiator that radiates the refrigerant discharged from the compression mechanism (30) to the indoor air
- the outdoor heat exchanger (21) constitutes a heat absorption side heat exchanger that functions as a heat absorber that absorbs heat from the outdoor air by evaporating the refrigerant decompressed by the expansion mechanism (40).
- the outdoor air and the indoor air constitute a medium that exchanges heat with the refrigerant.
- the four ports of the four-way selector valve (2a) are connected to the discharge side and the suction side of the compression mechanism (30), the outdoor heat exchanger (21), and the indoor heat exchanger (23) as refrigerant pipes ( 24) connected.
- the discharge side of the compression mechanism (30) communicates with the outdoor heat exchanger (21)
- the indoor heat exchanger (23) communicates with the suction side of the compression mechanism (30). Cooling operation (see the solid line in Fig. 1), the discharge side of the compression mechanism (30) and the indoor heat exchanger (23) communicate with each other, and the outdoor heat exchanger (21) (21) and the compression mechanism (30) It switches to the heating operation state (refer to the broken line in Fig. 1) that communicates with the suction side.
- the first throttle mechanism (41) and the second throttle mechanism (42) constitute an expansion mechanism (40), and are each composed of an expansion valve having a variable opening degree, that is, a throttle amount. Is configured to be variable.
- the first throttle mechanism (41) constitutes a high pressure side throttle mechanism
- the second throttle mechanism (42) constitutes a low pressure side throttle mechanism.
- the above The second throttle mechanism (42) constitutes a high pressure side throttle mechanism
- the first throttle mechanism (41) constitutes a low pressure side throttle mechanism.
- the first throttle mechanism (41) constitutes a heat source side throttle mechanism
- the second throttle mechanism (42) constitutes a utilization side throttle mechanism.
- the gas-liquid separator (22) is provided in a refrigerant pipe (24) between the first throttle mechanism (41) and the second throttle mechanism (42), and the gas refrigerant and liquid refrigerant in an intermediate pressure state And are configured to be separated from each other.
- One end of an instruction passage (25) is connected to the gas-liquid separator (22), and the other end of the instruction passage (25) is connected to an intermediate pressure region of the compressor (32).
- the injection passage (25) is configured to guide the gas refrigerant separated by the gas-liquid separator (22) to an intermediate pressure region of the compressor (32).
- the refrigerant circuit (20) is provided with various sensors. Specifically, the refrigerant pipe (24) on the discharge side of the compression mechanism (30) is provided with a high pressure sensor (51) for detecting the high pressure refrigerant pressure, and the refrigerant pipe on the suction side of the compression mechanism (30). (24) is provided with a low pressure sensor (52) for detecting the low pressure refrigerant pressure.
- the refrigerant pipe (24) on the indoor heat exchanger (23) side of the outdoor heat exchanger (21) is provided with a first refrigerant temperature sensor (53) force S, and the suction of the compression mechanism (30)
- the refrigerant pipe (24) on the side is provided with a second refrigerant temperature sensor (54), and an outdoor air temperature sensor (55) is provided on the air suction side of the outdoor heat exchanger (21).
- the refrigerant pipe (24) on the outdoor heat exchanger (21) side of the indoor heat exchanger (23) is provided with a third refrigerant temperature sensor (56), and the indoor heat exchanger (23)
- An indoor temperature sensor (57) is provided on the air suction side.
- the first refrigerant temperature sensor (53) is configured to calculate the refrigerant temperature of the outdoor heat exchanger (21) during the cooling operation and the inlet refrigerant temperature of the outdoor heat exchanger (21) during the heating operation. To detect.
- the third refrigerant temperature sensor (56) detects the outlet refrigerant temperature of the indoor heat exchanger (23) during the heating operation and the inlet refrigerant temperature of the indoor heat exchanger (23) during the cooling operation.
- the second refrigerant temperature sensor (54) detects the suction refrigerant temperature of the compression mechanism (30), that is, detects the refrigerant temperature at the outlet of the indoor heat exchanger (23) during the cooling operation.
- the refrigerant temperature at the outlet of the outdoor heat exchanger (21) during operation is detected.
- the outdoor temperature sensor (55) detects the temperature of the air sucked by the outdoor heat exchanger (21), and specifically, the outdoor air temperature that is the inlet medium temperature of the outdoor heat exchanger (21), that is, Detect the outside air temperature.
- the indoor temperature sensor (57) detects the temperature of the air sucked by the indoor heat exchanger (23), specifically, the indoor air temperature that is the inlet medium temperature of the indoor heat exchanger (23), that is, Detect the room temperature.
- the air conditioner (10) is provided with a controller (60) for controlling the refrigerant circuit (20).
- the controller (60) receives a sensor signal from the high pressure sensor (51) and the like, and includes a high pressure controller (61) and a capacity controller (62).
- the high-pressure control unit (61) constitutes a high-pressure control means, and includes a first control unit (6a) and a second control unit (6b).
- the first control unit (6a) includes the outlet refrigerant temperature of the outdoor heat exchanger (21), which serves as a radiator during cooling operation, and the intake air temperature (inlet medium temperature) of the outdoor heat exchanger (21).
- the target value of the high-pressure refrigerant pressure in the refrigerant circuit (20) is derived on the basis of the outside air temperature and the first throttle mechanism (41) as the high-pressure side throttle mechanism so that the high-pressure refrigerant pressure becomes the target value. Adjust the throttle amount to control the high pressure.
- the first control unit (6a) includes an outlet refrigerant temperature of the indoor heat exchanger (23) that serves as a radiator during heating operation, and an intake air temperature (inlet medium) of the indoor heat exchanger (23).
- the target value of the high-pressure refrigerant pressure of the refrigerant circuit (20) is derived based on the indoor temperature, which is the temperature), and the second throttle mechanism (42) that is the high-pressure side throttle mechanism so that the high-pressure refrigerant pressure becomes the target value. ) Adjust the throttle amount to perform high pressure control.
- the second control unit (6b) is based on the inlet refrigerant temperature of the indoor heat exchanger (23) serving as a heat absorber during the cooling operation and the outlet refrigerant temperature of the indoor heat exchanger (23).
- the throttle amount of the second throttle mechanism (42), which is the low-pressure side throttle mechanism, is adjusted so that the degree of superheat of the outlet refrigerant of the indoor heat exchanger (23) becomes a predetermined value.
- the second control unit (6b) is based on the inlet refrigerant temperature of the outdoor heat exchanger (21) serving as a heat absorber during the heating operation and the outlet refrigerant temperature of the outdoor heat exchanger (21).
- the first throttle mechanism low-pressure side throttle mechanism so that the degree of superheat of the outlet refrigerant of the outdoor heat exchanger (21) becomes a predetermined value. Adjust the aperture in 41).
- the capacity control unit (62) constitutes capacity control means.
- the capacity control unit (62) is configured to increase / decrease the operating capacity of the compressor (32) based on the capacity up signal and the capacity down signal output from the indoor unit (1B).
- the indoor unit (1B) is configured to output a capacity up signal and a capacity down signal based on the indoor temperature, which is the intake air temperature of the indoor heat exchanger (23), and the indoor set temperature. Yes.
- the refrigerant circuit (20) has a supercritical cycle.
- the cooling capacity of the refrigerant circuit (20) is constant, if the high-pressure refrigerant pressure in the refrigerant circuit (20) increases, the outdoor heat exchange that is a radiator (gas cooler)
- the outlet refrigerant temperature of the vessel (21) decreases.
- Fig. 4 shows the relationship between high-pressure refrigerant pressure and outlet refrigerant temperature for each cooling capacity when the outside air temperature is 30 ° C
- Fig. 5 shows each cooling capacity when the outside air temperature is 35 ° C. The relationship between the high-pressure refrigerant pressure and the outlet refrigerant temperature is shown.
- the optimum COP (optimum operating efficiency) cannot be determined based on the outlet refrigerant temperature of the outdoor heat exchanger (21).
- FIG. 6 shows the relationship between the high-pressure refrigerant pressure and COP for each cooling capacity when the outside air temperature is 30 ° C.
- FIG. 7 shows the case when the outside air temperature is 35 ° C.
- Line A shows the optimum COP high-pressure refrigerant pressure.
- Fig. 8 shows the relationship between the outlet refrigerant temperature and COP for each cooling capacity when the outside air temperature is 30 ° C
- Fig. 9 shows the cooling capacity when the outside air temperature is 35 ° C. It shows the relationship between the refrigerant temperature and COP for each.
- Line B shows the optimal COP outlet refrigerant temperature.
- the relationship between the high-pressure refrigerant pressure and the outlet refrigerant temperature is determined by the outside air temperature.
- the target high-pressure refrigerant pressure for the optimal COP is determined by the outside air temperature, the outlet refrigerant temperature, and the high-pressure refrigerant pressure.
- the high pressure of the refrigerant circuit (20) that is the optimum COP is determined by the outside air temperature that is the intake air temperature of the outdoor heat exchanger (21) and the outlet refrigerant temperature of the outdoor heat exchanger (21).
- the target value of the refrigerant pressure is derived.
- the opening degree (throttle amount) of the first throttling mechanism (41) is adjusted so that the high-pressure refrigerant pressure becomes the target value.
- the four-way selector valve (2a) is switched to the solid line side in FIG.
- the refrigerant discharged from the compressor (32) is cooled by radiating heat to the outdoor air in the outdoor heat exchanger (21).
- the pressure is reduced at (41) to an intermediate pressure state and flows into the gas-liquid separator (22).
- this gas-liquid separator (22) it is separated into a gas refrigerant and a liquid refrigerant, and the liquid refrigerant is depressurized by the second throttle mechanism (42) and flows to the indoor heat exchanger (23) to evaporate.
- the evaporated gas refrigerant returns to the compressor (32) and is compressed again.
- the gas refrigerant of the gas-liquid separator (22) is introduced into the intermediate pressure region of the compressor (32). This operation is repeated to cool the room.
- the four-way selector valve (2a) switches to the broken line side in FIG.
- the refrigerant discharged from the compressor (32) dissipates heat to the indoor air in the indoor heat exchanger (23) and is cooled, and the second throttle mechanism
- the pressure is reduced at (42) to an intermediate pressure state and flows into the gas-liquid separator (22).
- the gas-liquid separator (22) the gas refrigerant and the liquid refrigerant are separated, and the liquid refrigerant is depressurized by the first throttle mechanism (41), flows to the outdoor heat exchanger (21), and evaporates.
- the evaporated gas refrigerant returns to the compressor (32) and is compressed again.
- the gas refrigerant of the gas-liquid separator (22) is introduced into the intermediate pressure region of the compressor (32). This operation is repeated to heat the room.
- the control operation of the first throttle mechanism (41) and the second throttle mechanism (42) and the control operation of the operation capacity of the compression mechanism (30) are based on the control flow of FIGS. explain.
- step ST1 the outside air temperature sensor (55) detects the outside air temperature that is the intake air temperature of the outdoor heat exchanger (21), and at the same time, The first refrigerant temperature sensor (53) detects the outlet refrigerant temperature of the outdoor heat exchanger (21). Subsequently, the process proceeds to step ST2, and the first control unit (6a) derives a target value for the high-pressure refrigerant pressure based on the outside air temperature and the outlet refrigerant temperature.
- step ST3 the first control unit (6a) determines whether or not the high-pressure refrigerant pressure detected by the high-pressure sensor (51) is larger than a target value.
- the process proceeds from step ST3 to step ST4, the opening degree of the first throttle mechanism (41) is reduced, that is, the throttle amount is increased and the process returns to step ST1.
- step ST5 the opening degree of the first throttle mechanism (41) is increased, that is, the throttle amount is decreased and the process returns to step ST1. This operation is repeated to adjust the opening of the first throttle mechanism (41).
- step ST6 the third refrigerant temperature sensor (56) detects the inlet refrigerant temperature of the indoor heat exchanger (23), and the second refrigerant temperature sensor (54) detects the indoor heat exchanger (23 ) Outlet refrigerant temperature, that is, the suction refrigerant temperature of the compression mechanism (30).
- step ST7 the second controller (6b) derives the degree of superheat of the outlet refrigerant of the indoor heat exchanger (23), which is the degree of superheat of evaporation, based on the inlet refrigerant temperature and the outlet refrigerant temperature.
- step ST8 the second control unit (6b) determines whether or not the superheat degree is greater than a predetermined value (target superheat degree). If the degree of superheat is smaller than the predetermined value, the process proceeds from step ST8 to step ST9, the opening of the second throttle mechanism (42) is reduced, that is, the throttle amount is increased and the process returns to step ST6.
- a predetermined value target superheat degree
- step ST8 the opening degree of the second throttling mechanism (42) is increased, that is, the throttling amount is decreased and the process returns to step ST6. This operation is repeated to adjust the opening of the second throttle mechanism (42).
- step ST11 the indoor temperature sensor (57) detects the indoor air temperature (indoor temperature) which is the intake air temperature of the indoor heat exchanger (23) and sets the indoor temperature to the set temperature. Read degrees. Subsequently, the process proceeds to step ST12, and the indoor unit (1B) outputs a capacity up signal when the room temperature is higher than the set temperature, and outputs a capacity down signal when the room temperature is lower than the set temperature.
- indoor air temperature indoor temperature
- step ST13 the capacity control unit (62) determines whether the output of the indoor unit (1B) is a force that is a capability up signal or a capability down signal. If the output of the indoor unit (1 B) is a capacity-up signal, the process moves from step ST13 to step ST14, increasing the operating capacity of the compression mechanism (30), that is, increasing the rotational speed of the compressor (32). Return to step ST11.
- step ST13 If the output of the indoor unit (1B) is a capacity down signal, the process moves from step ST13 to step ST15, and the operating capacity of the compression mechanism (30) is reduced, that is, the rotation of the compressor (32). Decrease the number and return to step ST11. Repeat this operation to adjust the operating capacity of the compression mechanism (30).
- step ST21 the indoor temperature sensor (57) detects the indoor temperature, which is the intake air temperature of the indoor heat exchanger (23), and 3
- the refrigerant temperature sensor (56) detects the outlet refrigerant temperature of the indoor heat exchanger (23). Subsequently, the process proceeds to step ST22, and the first control unit (6a) derives a target value for the high-pressure refrigerant pressure based on the room temperature and the outlet refrigerant temperature.
- step ST23 in which the first controller (6a) determines whether or not the high-pressure refrigerant pressure detected by the high-pressure sensor (51) is greater than a target value.
- the process proceeds from step ST23 to step ST24, the opening degree of the second throttle mechanism (42) is reduced, that is, the throttle amount is increased and the process returns to step ST21.
- step ST23 the opening degree of the second throttle mechanism (42) is increased, that is, the throttle amount is decreased and the process returns to step ST21. . This operation is repeated to adjust the opening of the second throttle mechanism (42).
- step ST26 the first refrigerant temperature sensor (53) detects the inlet refrigerant temperature of the outdoor heat exchanger (21), and the second refrigerant temperature sensor (54) detects the outdoor heat exchanger (21 ) Outlet refrigerant temperature, that is, the suction refrigerant temperature of the compression mechanism (30).
- step ST27 the second control unit (6b) performs steaming based on the inlet refrigerant temperature and the suction refrigerant temperature.
- the degree of superheat of the outlet refrigerant of the outdoor heat exchanger (21) which is the degree of superheat, is derived.
- step ST28 in which the second control unit (6b) determines whether or not the degree of superheat is greater than a predetermined value (target degree of superheat). If the degree of superheat is smaller than the predetermined value, the process proceeds from step ST28 to step ST29, the opening degree of the first throttle mechanism (41) is decreased, that is, the throttle amount is increased, and the process returns to step ST26.
- a predetermined value target degree of superheat
- step ST28 the opening degree of the first throttle mechanism (41) is increased, that is, the throttle amount is decreased and the process returns to step ST26. Repeat this operation to adjust the opening of the first throttle mechanism (41).
- step ST31 the indoor temperature sensor (57) detects the indoor temperature that is the intake air temperature of the indoor heat exchanger (23) and reads the set temperature of the indoor temperature. Subsequently, the process proceeds to step ST32, and the indoor unit (1B) outputs a capacity up signal when the room temperature is lower than the set temperature, and outputs a capacity down signal when the room temperature is equal to or higher than the set temperature.
- step ST33 the capacity control section (62) determines whether the output of the indoor unit (1B) is a force that is a capability up signal or a capability down signal. If the output of the indoor unit (1 B) is a capacity increase signal, the process proceeds from step ST33 to step ST34, and the operating capacity of the compression mechanism (30) is increased, that is, the rotational speed of the compressor (32) is increased. Return to step ST31.
- step ST35 the operating capacity of the compression mechanism (30) is reduced, that is, the compressor (32) is rotated. Decrease the number and return to step ST31. Repeat this operation to adjust the operating capacity of the compression mechanism (30).
- the target value of the high pressure refrigerant pressure is determined by the intake air temperature (outside air temperature) of the outdoor heat exchanger (21) and the outlet refrigerant temperature of the outdoor heat exchanger (21) during the cooling operation.
- the target value of the high-pressure refrigerant pressure is derived from the intake air temperature (indoor temperature) of the indoor heat exchanger (23) and the outlet refrigerant temperature of the indoor heat exchanger (23) during heating operation.
- the throttle of the expansion mechanism (40) is adjusted so that the high-pressure refrigerant pressure becomes a target value. Since the amount is adjusted, it is possible to operate in an operating state where the operating efficiency (COP) is optimal.
- the first throttle mechanism (41) performs high pressure control during cooling operation, and the second throttle mechanism (42) performs superheat control, while the second throttle mechanism (42) performs high pressure control during heating operation. Since the superheat degree control is performed by the first throttle mechanism (41), the high-pressure refrigerant and the low-pressure refrigerant can be maintained in optimum states.
- the high-pressure refrigerant pressure can be adjusted reliably. it can.
- the refrigerant in the first embodiment flows in both directions through the expansion mechanism (40) and the gas-liquid separator (22). ) And gas-liquid separator (22) always flow in a certain direction.
- the refrigerant circuit (20) includes a rectifier circuit (2b).
- the rectifier circuit (2b) is configured as a bridge circuit having four flow paths with one-way valves.
- the first connection point of the rectifier circuit (2b) is connected to the outdoor heat exchanger (21), and the second connection point is connected to the indoor heat exchanger (23).
- a one-way passage (2c) is connected between the third connection point and the fourth connection point of the rectifier circuit (2b).
- An upstream force first throttle mechanism (41), a gas-liquid separator (22), and a second throttle mechanism (42) are sequentially connected to the negative direction passage (2c).
- the refrigerant flows from the first throttle mechanism (41) through the gas-liquid separator (22) through the second throttle mechanism (42) in both the cooling operation and the heating operation.
- the upstream side of the one-way passage (2c) is connected to the upper part of the gas-liquid separator (22), and the downstream side of the one-way passage (2c) is connected to the lower part.
- the first throttle mechanism (41) always constitutes a high-pressure side throttle mechanism
- the second throttle mechanism ( 42) always constitutes a low pressure side throttle mechanism
- the first control unit (6a) of the high-pressure control unit (61) ensures that the high-pressure refrigerant pressure of the refrigerant circuit (20) becomes the target value in both the cooling operation and the heating operation.
- High pressure control is performed by adjusting the aperture amount of the first aperture mechanism (41), which is the high pressure side aperture mechanism.
- the second control unit (6b) of the high-pressure control unit (61) is a low-pressure side throttling mechanism so that the refrigerant superheat degree becomes a predetermined value regardless of whether the cooling operation or the heating operation is performed. 2Adjust the iris of the iris mechanism (42).
- the compression mechanism (30) includes a low-stage compressor (33) and a high-stage compressor (34), and the injection passage (25) includes the low-stage compressor (33). And a high-stage compressor (34).
- Other configurations and operational effects are the same as those of the first embodiment.
- the refrigerant of the first embodiment flows in both directions through the gas-liquid separator (22), but the refrigerant always keeps the gas-liquid separator (22) constant. It is designed to flow in the direction.
- the refrigerant circuit (20) includes a switching mechanism (2d) for switching the refrigerant flow.
- the switching mechanism (2d) is composed of a four-way switching valve, and two of the four ports are connected to the outdoor heat exchanger (21) via the first throttle mechanism (41), and the second throttle It is connected to the indoor heat exchanger (23) via the mechanism (42).
- a one-way passage (2c) is connected between the other two ports of the switching mechanism (2d).
- a gas-liquid separator (22) is provided in the -direction passage (2c).
- An upstream side of the one-way passage (2c) is connected to the upper portion of the gas-liquid separator (22), and a downstream side of the one-way passage (2c) is connected to the lower portion.
- the refrigerant flows in one direction through the gas-liquid separator (22) during both the cooling operation and the heating operation.
- Other configurations and operational effects are the same as those of the first embodiment.
- Embodiment 4 of the present invention will be described in detail based on the drawings.
- the above embodiments:! To 3 are provided with a plurality of indoor units (1B) instead of being provided with a single indoor unit (1B). It is a multi-type.
- the rectifier circuit (2b) of the second embodiment is provided, and a plurality of indoor heat exchangers (23) are provided in the refrigerant circuit (20).
- each indoor unit (1B) is connected in parallel to each other, and each indoor unit (1B) is connected to the outdoor unit (1A).
- Each indoor unit (1B) houses an indoor heat exchanger (23) and a second throttle mechanism (42) connected in series to the indoor heat exchanger (23).
- a first throttle mechanism (41) is provided in the refrigerant pipe (24) between the outdoor heat exchanger (21) of the outdoor unit (1A) and the rectifier circuit (2b).
- the first throttle mechanism (41) is a heat source side throttle mechanism
- the second throttle mechanism (42) is a user side throttle mechanism.
- the first diaphragm mechanism (41) constitutes a high pressure side diaphragm mechanism
- the second diaphragm mechanism (42) constitutes a low pressure side diaphragm mechanism.
- the second throttle mechanism (42) constitutes a high pressure side throttle mechanism
- the first throttle mechanism (41) constitutes a low pressure side throttle mechanism.
- Each indoor unit (1B) is provided with a third refrigerant temperature sensor (56) and an indoor temperature sensor (57), as well as the compression of the indoor heat exchanger (23), as in the first embodiment.
- a fourth refrigerant temperature sensor (58) is provided in the refrigerant pipe (24) on the mechanism (30) side. The fourth refrigerant temperature sensor (58) detects the outlet refrigerant temperature of the indoor heat exchanger (23) during the heating operation.
- the controller (60) of the air conditioner (10) includes an outlet temperature controller (63) in addition to the high pressure controller (61) and the capacity controller (62).
- the high-pressure control section (61) performs high-pressure control and superheat control in the same manner as in the first embodiment during the cooling operation.
- the outlet temperature control section (63) constitutes outlet temperature control means, and includes a first control section (6c) and a second control section (6d).
- the first control unit (6c) is configured to set the indoor temperature, which is the intake air temperature of the indoor heat exchanger (23), which serves as a radiator during heating operation, and the set pressure of the high-pressure refrigerant pressure of the refrigerant circuit (20). And a target value for the outlet refrigerant temperature of the indoor heat exchanger (23) is derived based on the The outlet temperature is controlled by adjusting the throttle amount of the second throttle mechanism (42), which is the high-pressure side throttle mechanism, so that the value is the same.
- the second control unit (6d) is based on the inlet refrigerant temperature of the outdoor heat exchanger (21) serving as a heat absorber during heating operation and the outlet refrigerant temperature of the outdoor heat exchanger (21).
- the throttle amount of the first throttle mechanism (41) which is the low-pressure side throttle mechanism, is adjusted so that the degree of superheat of the outlet refrigerant of the outdoor heat exchanger (21) becomes a predetermined value.
- the optimum COP is determined by the room temperature (the outside air temperature described in the first embodiment), the outlet refrigerant temperature, and the high-pressure refrigerant pressure. Therefore, the first control unit (6c) is optimal in the heating operation depending on the indoor temperature that is the intake air temperature of the indoor heat exchanger (23) and the set pressure value of the high-pressure refrigerant pressure of the refrigerant circuit (20).
- the target value for the outlet refrigerant temperature of the indoor heat exchanger (23), which is the COP, is derived. Then, the opening degree (throttle amount) of the second throttle mechanism (42) is adjusted so that the outlet refrigerant temperature becomes the target value.
- the capacity control unit (62) constitutes a capacity control means.
- the capacity control unit (62) controls the operating capacity of the compression mechanism (30) so that the low-pressure refrigerant pressure of the refrigerant circuit (20) becomes a set pressure value during the cooling operation, and at the same time the refrigerant circuit (20
- the operating capacity of the compression mechanism (30) is controlled so that the high-pressure refrigerant pressure of) reaches the set pressure value.
- the capacity control section (62) reduces the set pressure value of the low-pressure refrigerant pressure during the cooling operation based on the capacity increase signal output from the indoor unit (1B), and the high-pressure refrigerant during the heating operation. While the set pressure value of the pressure is increased, the set pressure value of the low-pressure refrigerant pressure during cooling operation is increased based on the capacity down signal output by the indoor unit (1B), and the high-pressure refrigerant pressure during heating operation is increased. Reduce the set pressure value.
- the capacity controller (62) changes the set pressure value and outputs a capacity down signal when the ratio of the number of indoor units (1B) that output the capacity up signal reaches 20 to 40%.
- the ratio of the number of indoor units (1B) to be reached is 20 to 40%, the set pressure value is changed.
- each indoor unit (1B) outputs a capacity-up signal when the opening of the second throttle mechanism (42) reaches 80 to 90% or more of the full opening, and the second throttle mechanism (42) It is configured to output a capability down signal when the opening is 10 to 20% or less of the total opening.
- Driving action is the same as those in the first embodiment.
- the four-way selector valve (2a) switches to the solid line side in FIG.
- the refrigerant discharged from the compressor (32) is cooled by releasing heat to the outdoor air in the outdoor heat exchanger (21), and is reduced in pressure to the intermediate pressure state by the first throttle mechanism (41).
- the gas-liquid separator (22) the gas refrigerant and the liquid refrigerant are separated.
- the liquid refrigerant flows into each indoor unit (1B), is depressurized by the second throttle mechanism (42), and is evaporated by the plurality of indoor heat exchangers (23).
- the evaporated gas refrigerant returns to the compressor (32) and is compressed again.
- the gas refrigerant in the gas-liquid separator (22) is introduced into the intermediate pressure region of the compressor (32). Repeat this operation to cool the room.
- the four-way selector valve (2a) switches to the broken line in FIG.
- the refrigerant discharged from the compressor (32) flows to each indoor unit (1B), is radiated to the indoor air by the plurality of indoor heat exchangers (23), is cooled, and is depressurized by the second throttle mechanism (42).
- the pressure becomes intermediate and flows into the gas-liquid separator (22).
- this gas-liquid separator (22) it is separated into a gas refrigerant and a liquid refrigerant, and the liquid refrigerant is decompressed by the first throttle mechanism (41) and flows to the outdoor heat exchanger (21) to evaporate.
- the evaporated gas refrigerant returns to the compressor (32) and is compressed again.
- the gas refrigerant of the gas-liquid separator (22) is introduced into the intermediate pressure region of the compressor (32). Repeat this operation to heat the room.
- steps ST41 to ST50 are the same as steps ST1 to ST10 shown in FIG.
- the outside air temperature sensor (55) detects the outside air temperature and the first refrigerant temperature sensor.
- step ST41 the first control unit (6a) of the high pressure control unit (61) derives a target value for the high pressure refrigerant pressure based on the outside air temperature and the outlet refrigerant temperature (step ST42).
- the first control unit (6a) determines whether or not the high-pressure refrigerant pressure detected by the high-pressure sensor (51) is larger than the target value (step ST43), and if the high-pressure refrigerant pressure is smaller than the target value, Reduce the opening of the first throttle mechanism (41) ( Step ST44) When the high-pressure refrigerant pressure is equal to or higher than the target value, the opening of the first throttle mechanism (41) is increased (step ST45). This operation is repeated to adjust the opening of the first throttle mechanism (41).
- the third refrigerant temperature sensor (56) detects the inlet refrigerant temperature of the indoor heat exchanger (23), and the fourth refrigerant temperature sensor (58) detects the outlet refrigerant temperature of the indoor heat exchanger (23). Is detected (step ST46).
- the second control unit (6b) of the high pressure control unit (61) is connected to the outlet refrigerant of the indoor heat exchanger (23), which is based on the inlet refrigerant temperature and the outlet refrigerant temperature.
- the degree of superheat is derived (step ST47). Thereafter, the second control unit (6b) determines whether or not the degree of superheat is greater than a predetermined value (step ST48).
- the opening degree of the second throttle mechanism (42) is determined. If the degree of superheat is equal to or greater than a predetermined value, the opening degree of the second throttle mechanism (42) is increased (step ST50). This operation is repeated to adjust the opening of the second throttle mechanism (42).
- the low pressure sensor (52) detects the low pressure refrigerant pressure (step ST51), and the capacity control section (62) determines whether or not the low pressure refrigerant pressure is larger than the set pressure value (step ST52). If the low-pressure refrigerant pressure is smaller than the set pressure value, reduce the rotation speed of the compressor (32) (step ST53) . If the low-pressure refrigerant pressure is higher than the set pressure value, reduce the rotation speed of the compressor (32). Increase (Step ST54) and repeat this operation to adjust the operating capacity of the compression mechanism (30).
- each indoor temperature sensor (57) is set to the intake air temperature of each indoor heat exchanger (23).
- a room temperature is detected (step ST61).
- the first control unit (6c) of the outlet temperature control unit (63) determines the target value of the outlet refrigerant temperature of each indoor heat exchanger (23) based on the set pressure value of the high-pressure refrigerant pressure and the indoor temperature. Derived (step ST62).
- the first controller (6c) of the outlet temperature controller (63) determines that the outlet refrigerant temperature of the indoor heat exchanger (23) detected by the third refrigerant temperature sensor (56) is larger than the target value. (Step ST63). If the outlet refrigerant temperature is lower than the target value, the opening of the second throttle mechanism (42) is increased (step ST64), that is, the throttle amount is decreased and the process returns to step ST61.
- step ST65 the opening of the second throttle mechanism (42) is reduced (step ST65), that is, the throttle amount is increased and the process returns to step ST61. Repeat this action Adjust the opening of the second throttle mechanism (42).
- the first refrigerant temperature sensor (53) detects the inlet refrigerant temperature of the outdoor heat exchanger (21)
- the second refrigerant temperature sensor (54) detects the outlet refrigerant temperature of the outdoor heat exchanger (21). That is, the suction refrigerant temperature of the compression mechanism (30) is detected (step ST66).
- the second control section (6d) of the outlet temperature control section (63) is controlled by the outlet refrigerant of the outdoor heat exchanger (21), which has the superheated evaporation temperature based on the inlet refrigerant temperature and the suction refrigerant temperature.
- the degree of superheat of is derived (step ST67).
- the second controller (6d) of the outlet temperature controller (63) determines whether or not the degree of superheat is greater than a predetermined value (target degree of superheat) (step ST68).
- a predetermined value target degree of superheat
- step ST70 the opening degree of the first throttle mechanism (41) is increased (step ST70), that is, the throttle amount is decreased and the process returns to step ST66. Repeat this operation to adjust the opening of the first throttling mechanism (41).
- the high pressure sensor (51) detects the high pressure refrigerant pressure (step ST71), determines whether the high pressure refrigerant pressure is larger than the set pressure value (step ST72), and sets the high pressure refrigerant pressure. If the pressure value is smaller, increase the rotation speed of the compressor (32) (step ST51) . If the high-pressure refrigerant pressure is higher than the set pressure value, decrease the rotation speed of the compressor (32) (step ST52). This operation is repeated to adjust the operating capacity of the compression mechanism (30).
- the target set pressure value decreases the set pressure value of the low-pressure refrigerant pressure during the cooling operation based on the capacity increase signal output from each indoor unit (1B). Increase the set pressure value of the high-pressure refrigerant pressure during heating operation, while increasing the set pressure value of the low-pressure refrigerant pressure during cooling operation based on the capacity down signal output by the indoor unit (1B) Decrease the set pressure value of the high pressure refrigerant pressure.
- each indoor unit (1B) outputs a capacity-up signal when the opening of the second throttle mechanism (42) becomes 80 to 90% or more of the total opening, and the second throttle mechanism (42 ) Outputs a capability down signal when the opening of 10) falls below 10 to 20% of the total opening.
- the capacity control section (62) of the indoor unit (1B) that outputs the capacity increase signal The set pressure value is changed when the ratio of the number becomes 20 to 40%, while the set pressure value is changed when the ratio of the number of indoor units (1B) that output the capacity down signal becomes 20 to 40%.
- the target value of the outlet refrigerant temperature of each indoor heat exchanger (23) is set by the set pressure value of the high-pressure refrigerant pressure of the refrigerant circuit (20) and the room temperature. Since the second throttle mechanism (42) is adjusted so that the outlet refrigerant temperature reaches the target value, the heating operation efficiency (COP) can be operated in the optimum operating state.
- the present embodiment is configured such that two compressors (32) are provided in place of the one compressor (32) in the fourth embodiment. is there.
- the compression mechanism (30) includes a low-stage compressor (33) and a high-stage compressor (34).
- the injection passage (25) includes the low-stage compressor (33) and the high-stage compressor.
- a switching mechanism (2d) is provided instead of the rectifier circuit (2b) in the fourth embodiment.
- the switching mechanism (2d) includes a four-way switching valve, and two of the four ports are connected to the outdoor heat exchanger (21 via the first throttle mechanism (41). ) And connected to each indoor heat exchanger (23) via the second throttle mechanism (42).
- a one-way passage (2c) is connected between the other two ports of the switching mechanism (2d).
- a gas-liquid separator (22) is provided in the -direction passage (2c).
- An upstream side of the one-way passage (2c) is connected to the upper portion of the gas-liquid separator (22), and a downstream side of the one-way passage (2c) is connected to the lower portion.
- the present invention is not limited to the fourth embodiment with respect to the above-described fourth embodiment, but the conditions of the capability up signal and the capability down signal output by each indoor unit (1B).
- the capacity control of the compression mechanism (30) is not limited to only changing the set pressure value.
- the air conditioners (10) of Embodiments 1 to 3 may be cooling only machines or heating only machines. At that time, in the case of a heating-only machine, the outlet temperature control unit (63) of Embodiment 4 may be applied instead of the high-pressure control unit (61).
- the high pressure control unit (61) in each embodiment derives a target value of the high pressure refrigerant pressure based on the outlet refrigerant temperature of the heat radiation side heat exchanger and the inlet medium temperature of the heat radiation side heat exchanger. I will do it. However, the high pressure control unit (61) adds the refrigerant temperature equivalent saturation pressure in the heat absorption side heat exchanger to the parameter, and based on the outlet refrigerant temperature, the inlet medium temperature, and the refrigerant temperature equivalent saturation pressure, The target value of the high-pressure refrigerant pressure in (20) may be derived. In this case, the target value of the high-pressure refrigerant pressure can be derived more accurately.
- the target of the high-pressure refrigerant pressure is based on the outlet refrigerant temperature of the outdoor heat exchanger (21), the outdoor air temperature, and the evaporation pressure or evaporation temperature in the indoor heat exchanger (23). A value may be derived.
- the target value of the high-pressure refrigerant pressure is derived based on the outlet refrigerant temperature of the indoor heat exchanger (23), the indoor temperature, and the evaporation pressure or evaporation temperature in the outdoor heat exchanger (21). Yes.
- the second controller (6b, 6d) in each embodiment performs superheat degree control.
- the first to third inventions are not limited to superheat control.
- the high pressure control and the outlet temperature control are performed by the first throttle mechanism (4
- the medium that exchanges heat with the refrigerant is not limited to air, and may be water, brine, or the like.
- the expansion mechanism (40), which is not limited to carbon dioxide, is not limited to an expansion valve.
- the present invention is useful as a countermeasure for operating efficiency in the refrigeration system of the supercritical refrigeration cycle.
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)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2007230272A AU2007230272B2 (en) | 2006-03-27 | 2007-03-26 | Refrigeration system |
CN2007800112310A CN101410677B (zh) | 2006-03-27 | 2007-03-26 | 冷冻装置 |
US12/225,577 US8418489B2 (en) | 2006-03-27 | 2007-03-26 | Control of supercritical refrigeration system |
ES07739659T ES2797950T3 (es) | 2006-03-27 | 2007-03-26 | Sistema de refrigeración |
EP07739659.6A EP2006614B1 (en) | 2006-03-27 | 2007-03-26 | Refrigeration system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006084958A JP5309424B2 (ja) | 2006-03-27 | 2006-03-27 | 冷凍装置 |
JP2006-084958 | 2006-03-27 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007111303A1 true WO2007111303A1 (ja) | 2007-10-04 |
Family
ID=38541220
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2007/056221 WO2007111303A1 (ja) | 2006-03-27 | 2007-03-26 | 冷凍装置 |
Country Status (8)
Country | Link |
---|---|
US (1) | US8418489B2 (ja) |
EP (1) | EP2006614B1 (ja) |
JP (1) | JP5309424B2 (ja) |
KR (1) | KR101070566B1 (ja) |
CN (1) | CN101410677B (ja) |
AU (1) | AU2007230272B2 (ja) |
ES (1) | ES2797950T3 (ja) |
WO (1) | WO2007111303A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2075518A3 (en) * | 2007-12-26 | 2013-03-20 | Sanyo Electric Co., Ltd. | Air conditioner |
EP2051027A3 (de) * | 2007-10-19 | 2014-11-19 | STIEBEL ELTRON GmbH & Co. KG | Wärmepumpenanlage |
CN112594792A (zh) * | 2020-12-22 | 2021-04-02 | 青岛海信日立空调***有限公司 | 一种空调室外机 |
Families Citing this family (27)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101402158B1 (ko) | 2008-01-28 | 2014-06-27 | 엘지전자 주식회사 | 공기조화 시스템 |
JP2012504746A (ja) * | 2008-10-01 | 2012-02-23 | キャリア コーポレイション | 遷臨界冷凍システムの高圧側圧力制御 |
JP5036790B2 (ja) * | 2009-11-16 | 2012-09-26 | 三菱電機株式会社 | 空気調和装置 |
KR20110092147A (ko) * | 2010-02-08 | 2011-08-17 | 삼성전자주식회사 | 공기조화기 및 그 제어방법 |
EP2545329A2 (en) * | 2010-03-08 | 2013-01-16 | Carrier Corporation | Capacity and pressure control in a transport refrigeration system |
CN102022851B (zh) * | 2010-12-22 | 2012-05-23 | 天津商业大学 | 双级压缩制冷*** |
JP5798830B2 (ja) * | 2011-07-29 | 2015-10-21 | 三菱重工業株式会社 | 超臨界サイクルヒートポンプ |
JP5240332B2 (ja) * | 2011-09-01 | 2013-07-17 | ダイキン工業株式会社 | 冷凍装置 |
JP5594267B2 (ja) * | 2011-09-12 | 2014-09-24 | ダイキン工業株式会社 | 冷凍装置 |
CN102506534B (zh) * | 2011-09-21 | 2013-09-11 | 中国科学院理化技术研究所 | 带一级分凝分离回热混合工质节流制冷的低温冷冻贮存箱 |
CN102518584B (zh) * | 2011-12-15 | 2014-08-06 | 上海维尔泰克螺杆机械有限公司 | 一种跨临界或超临界***用制冷压缩机试验台*** |
DE102011121859B4 (de) * | 2011-12-21 | 2013-07-18 | Robert Bosch Gmbh | Wärmepumpe mit zweistufigem Verdichter und Vorrichtung zum Umschalten zwischen Heiz- und Kühlbetrieb |
JP2013217631A (ja) * | 2012-03-14 | 2013-10-24 | Denso Corp | 冷凍サイクル装置 |
JP5617860B2 (ja) * | 2012-03-28 | 2014-11-05 | ダイキン工業株式会社 | 冷凍装置 |
JP6193555B2 (ja) * | 2012-11-09 | 2017-09-06 | 株式会社Soken | 冷凍サイクル装置 |
CN103808010A (zh) * | 2012-11-15 | 2014-05-21 | 珠海格力电器股份有限公司 | 准二级压缩热泵热水器及其控制方法 |
JP5889347B2 (ja) * | 2014-02-12 | 2016-03-22 | 三菱電機株式会社 | 冷凍サイクル装置及び冷凍サイクル制御方法 |
JP2016053437A (ja) * | 2014-09-03 | 2016-04-14 | 三菱電機株式会社 | 冷凍サイクル装置、及び、空気調和装置 |
JP6248878B2 (ja) * | 2014-09-18 | 2017-12-20 | 株式会社富士通ゼネラル | 空気調和装置 |
JP6548890B2 (ja) * | 2014-10-31 | 2019-07-24 | 三菱重工サーマルシステムズ株式会社 | 冷凍サイクルの制御装置、冷凍サイクル、及び冷凍サイクルの制御方法 |
WO2017017767A1 (ja) * | 2015-07-27 | 2017-02-02 | 三菱電機株式会社 | 空気調和装置 |
EP3159628A1 (de) * | 2015-10-20 | 2017-04-26 | Ulrich Brunner GmbH | Wärmepumpenkreislauf mit einem verdampfer |
US10830515B2 (en) * | 2015-10-21 | 2020-11-10 | Mitsubishi Electric Research Laboratories, Inc. | System and method for controlling refrigerant in vapor compression system |
JP2018071909A (ja) * | 2016-10-31 | 2018-05-10 | 三菱重工サーマルシステムズ株式会社 | 冷凍装置、冷凍システム |
CA3049596A1 (en) | 2018-07-27 | 2020-01-27 | Hill Phoenix, Inc. | Co2 refrigeration system with high pressure valve control based on coefficient of performance |
CN110986417A (zh) * | 2019-11-25 | 2020-04-10 | 珠海格力节能环保制冷技术研究中心有限公司 | 双补气热泵***及其控制方法 |
JP7437754B2 (ja) | 2020-05-29 | 2024-02-26 | パナソニックIpマネジメント株式会社 | 空気調和装置 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1089780A (ja) * | 1996-09-13 | 1998-04-10 | Mitsubishi Electric Corp | 冷凍システム装置 |
JPH11270918A (ja) * | 1998-03-24 | 1999-10-05 | Daikin Ind Ltd | 冷凍装置 |
JP2001133058A (ja) | 1999-11-05 | 2001-05-18 | Matsushita Electric Ind Co Ltd | 冷凍サイクル装置 |
JP2002156146A (ja) * | 2000-11-17 | 2002-05-31 | Mitsubishi Heavy Ind Ltd | 空気調和装置 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN1153276A (zh) * | 1995-12-25 | 1997-07-02 | 田岛工程株式会社 | 一种致冷*** |
EP0837291B1 (en) * | 1996-08-22 | 2005-01-12 | Denso Corporation | Vapor compression type refrigerating system |
JP3890713B2 (ja) * | 1997-11-27 | 2007-03-07 | 株式会社デンソー | 冷凍サイクル装置 |
JP3109500B2 (ja) * | 1998-12-16 | 2000-11-13 | ダイキン工業株式会社 | 冷凍装置 |
JP4258944B2 (ja) * | 1999-10-28 | 2009-04-30 | 株式会社デンソー | 超臨界蒸気圧縮機式冷凍サイクル |
CN1477353A (zh) * | 2003-04-17 | 2004-02-25 | 上海交通大学 | 空调制冷机故障的模糊诊断方法 |
JP4613526B2 (ja) * | 2004-06-23 | 2011-01-19 | 株式会社デンソー | 超臨界式ヒートポンプサイクル装置 |
JP4389699B2 (ja) * | 2004-07-07 | 2009-12-24 | ダイキン工業株式会社 | 冷凍装置 |
US7478539B2 (en) * | 2005-06-24 | 2009-01-20 | Hussmann Corporation | Two-stage linear compressor |
-
2006
- 2006-03-27 JP JP2006084958A patent/JP5309424B2/ja active Active
-
2007
- 2007-03-26 US US12/225,577 patent/US8418489B2/en active Active
- 2007-03-26 KR KR1020087022109A patent/KR101070566B1/ko not_active IP Right Cessation
- 2007-03-26 WO PCT/JP2007/056221 patent/WO2007111303A1/ja active Application Filing
- 2007-03-26 EP EP07739659.6A patent/EP2006614B1/en active Active
- 2007-03-26 CN CN2007800112310A patent/CN101410677B/zh not_active Expired - Fee Related
- 2007-03-26 AU AU2007230272A patent/AU2007230272B2/en not_active Ceased
- 2007-03-26 ES ES07739659T patent/ES2797950T3/es active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1089780A (ja) * | 1996-09-13 | 1998-04-10 | Mitsubishi Electric Corp | 冷凍システム装置 |
JPH11270918A (ja) * | 1998-03-24 | 1999-10-05 | Daikin Ind Ltd | 冷凍装置 |
JP2001133058A (ja) | 1999-11-05 | 2001-05-18 | Matsushita Electric Ind Co Ltd | 冷凍サイクル装置 |
JP2002156146A (ja) * | 2000-11-17 | 2002-05-31 | Mitsubishi Heavy Ind Ltd | 空気調和装置 |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2051027A3 (de) * | 2007-10-19 | 2014-11-19 | STIEBEL ELTRON GmbH & Co. KG | Wärmepumpenanlage |
EP2075518A3 (en) * | 2007-12-26 | 2013-03-20 | Sanyo Electric Co., Ltd. | Air conditioner |
CN112594792A (zh) * | 2020-12-22 | 2021-04-02 | 青岛海信日立空调***有限公司 | 一种空调室外机 |
Also Published As
Publication number | Publication date |
---|---|
KR20080094103A (ko) | 2008-10-22 |
EP2006614A9 (en) | 2009-07-22 |
JP2007263383A (ja) | 2007-10-11 |
AU2007230272B2 (en) | 2010-12-02 |
US20090260380A1 (en) | 2009-10-22 |
EP2006614A2 (en) | 2008-12-24 |
ES2797950T3 (es) | 2020-12-04 |
JP5309424B2 (ja) | 2013-10-09 |
AU2007230272A1 (en) | 2007-10-04 |
EP2006614A4 (en) | 2017-05-17 |
EP2006614B1 (en) | 2020-03-25 |
CN101410677A (zh) | 2009-04-15 |
KR101070566B1 (ko) | 2011-10-05 |
CN101410677B (zh) | 2010-12-08 |
US8418489B2 (en) | 2013-04-16 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5309424B2 (ja) | 冷凍装置 | |
US9341393B2 (en) | Refrigerating cycle apparatus having an injection circuit and operating with refrigerant in supercritical state | |
JP4457928B2 (ja) | 冷凍装置 | |
JP5411643B2 (ja) | 冷凍サイクル装置および温水暖房装置 | |
WO2016171052A1 (ja) | 冷凍サイクル装置 | |
JP4375171B2 (ja) | 冷凍装置 | |
WO2007110908A9 (ja) | 冷凍空調装置 | |
WO2006028218A1 (ja) | 冷凍装置 | |
WO2008032645A1 (fr) | dispositif de réfrigération | |
JP2006112708A (ja) | 冷凍空調装置 | |
JP4550153B2 (ja) | ヒートポンプ装置及びヒートポンプ装置の室外機 | |
JP4273493B2 (ja) | 冷凍空調装置 | |
EP2455688B1 (en) | Heat pump and method of controlling the same | |
JP2011196684A (ja) | ヒートポンプ装置及びヒートポンプ装置の室外機 | |
JP4887929B2 (ja) | 冷凍装置 | |
JP2009243881A (ja) | ヒートポンプ装置及びヒートポンプ装置の室外機 | |
JP4767340B2 (ja) | ヒートポンプ装置の制御装置 | |
JP2006145144A (ja) | 冷凍サイクル装置 | |
JP7375167B2 (ja) | ヒートポンプ | |
JP2019203688A (ja) | 冷凍サイクル装置 | |
KR100395026B1 (ko) | 히트펌프의 증발온도 보상장치 및 그 보상방법 | |
JP4752146B2 (ja) | 空気調和装置 | |
WO2024071214A1 (ja) | 冷凍サイクル装置 | |
JP5578914B2 (ja) | マルチ形空気調和装置 | |
JP4752145B2 (ja) | 空気調和装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 07739659 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: KR Ref document number: 1020087022109 Country of ref document: KR |
|
WWE | Wipo information: entry into national phase |
Ref document number: 12225577 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 200780011231.0 Country of ref document: CN |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2007230272 Country of ref document: AU |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2007739659 Country of ref document: EP |
|
ENP | Entry into the national phase |
Ref document number: 2007230272 Country of ref document: AU Date of ref document: 20070326 Kind code of ref document: A |