WO2001038801A1 - Dispositif de refrigeration - Google Patents

Dispositif de refrigeration Download PDF

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Publication number
WO2001038801A1
WO2001038801A1 PCT/JP2000/008279 JP0008279W WO0138801A1 WO 2001038801 A1 WO2001038801 A1 WO 2001038801A1 JP 0008279 W JP0008279 W JP 0008279W WO 0138801 A1 WO0138801 A1 WO 0138801A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
liquid
circuit
compressor
pressure
Prior art date
Application number
PCT/JP2000/008279
Other languages
English (en)
Japanese (ja)
Inventor
Masaki Yamamoto
Makoto Momosaki
Tatsuo Fujiwara
Original Assignee
Daikin Industries, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to EP00977900A priority Critical patent/EP1235043A1/fr
Priority to AU15503/01A priority patent/AU1550301A/en
Priority to KR1020027006628A priority patent/KR20020070982A/ko
Publication of WO2001038801A1 publication Critical patent/WO2001038801A1/fr

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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
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
    • F25B2313/02541—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements during cooling
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
    • F25B2313/02543—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements during heating
    • 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
    • F25B2313/031—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
    • F25B2400/04—Refrigeration circuit bypassing means
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/07—Exceeding a certain pressure value in a refrigeration component or 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
    • 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
    • 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
    • F25B2700/2115—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
    • 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

Definitions

  • the present invention relates to a refrigeration system using a non-azeotropic mixed refrigerant, and more particularly to a technique for stabilizing the composition of a non-azeotropic mixed refrigerant circulating in a refrigerant circuit.
  • Landscape technology
  • a refrigerant circuit of a refrigeration apparatus that performs a vapor compression refrigeration cycle generally includes a compressor, a condenser, an expansion valve, and an evaporator connected in order by a refrigerant pipe.
  • this type of refrigerant circuit has an accumulator attached to a suction pipe of a compressor.
  • the liquid refrigerant mixed with the low-pressure gas refrigerant is separated from the gas refrigerant. Therefore, as shown in FIG. 2, a part of the refrigerant in the circuit stays in the accumulator (1) in the state of the liquid refrigerant (RL).
  • a non-azeotropic mixed refrigerant such as R407C is formed by mixing a plurality of refrigerants having different boiling points. And, if the ratio of each composition refrigerant, that is, the composition ratio is different, the characteristics will be different. Therefore, the composition ratio of the non-azeotropic refrigerant mixture is strictly determined so that the refrigerant exhibits predetermined characteristics.
  • the low-pressure refrigerant flowing into the accumulator (1) is basically a gas refrigerant (RG), which includes a liquid refrigerant (RL).
  • the liquid refrigerant (RL) has a high composition ratio of the high boiling point refrigerant (R134a for R407C), which is difficult to evaporate due to the characteristics of non-azeotropic refrigerant mixture, and evaporates.
  • the composition ratio of the low boiling point refrigerant (R32 in the case of R407C) is low.
  • liquid refrigerant (RL) since the liquid refrigerant (RL) has a higher density than the gas refrigerant (RG), the liquid refrigerant contains a large amount of high-boiling-point refrigerant in the accumulator (1) where the refrigerant stays.
  • gas refrigerant (RG) has a significantly lower proportion of high-boiling refrigerants than the original composition ratio of non-azeotropic mixed refrigerants. Therefore, the gas refrigerant (RG) in which the ratio of the high-boiling refrigerant is low and the ratio of the low-boiling refrigerant is high flows out of the accumulator and is sucked into the compressor.
  • the non-azeotropic mixed refrigerant circulates in the refrigerant circuit in a state different from the original composition ratio.
  • a change in refrigerant characteristics may cause the refrigeration system to lose its original performance due to an increase in high-pressure pressure, etc., and may reduce the reliability of the refrigeration system, for example, resulting in inefficient operation. .
  • the present invention has been made in view of such a problem, and an object of the present invention is to stabilize the composition of a non-azeotropic mixed refrigerant flowing in a refrigerant circuit to improve the reliability of a refrigeration system. Is to prevent the property from being reduced. Disclosure of the invention
  • the refrigerant in a refrigeration apparatus using a non-azeotropic mixed refrigerant, is circulated in a refrigerant circuit while being stored in a storage unit such as a high-pressure receiver.
  • the solution taken by the present invention presupposes a refrigeration apparatus including a refrigerant circuit (12) for performing a vapor compression refrigeration cycle using a non-azeotropic mixed refrigerant.
  • the refrigeration apparatus has a configuration in which a high-pressure liquid line of the refrigerant circuit (12) is provided with a storage part (43) for discharging the liquid refrigerant while storing the refrigerant.
  • the refrigerant circuit (12) is configured as a refrigerant circuit (12) having no accumulator on the suction side of the compressor (21). That is, it is preferable to connect the outlet side of the evaporator (31, 23) directly to the suction side of the compressor (21). It should be noted that the term “direct” in this case is not used to mean a configuration other than connecting a four-way switching valve or the like between the evaporator (31, 23) and the compressor (21). This means that the evaporators (31, 23) and the compressor (21) are connected without passing through the accumulator.
  • a liquid seal prevention passage (27) is provided between the liquid pipe between the storage part (43) and the expansion mechanism (EV) and the discharge pipe of the compressor (21). It is preferable that the liquid seal prevention passage (27) is configured as a one-way passage that allows the refrigerant to flow from the liquid pipe side to the discharge pipe side.
  • the discharge pipe temperature sensor (Td), the condenser temperature sensor (Tc, Te), the evaporator temperature sensor (Te, Tc), and the expansion mechanism (EV) which is a component of the refrigerant circuit It is preferable to include a control means (50) for controlling the opening degree of each of the temperature sensors according to the output of each temperature sensor (Td, Tc, Te).
  • R407C can be used as the non-azeotropic mixed refrigerant.
  • the non-azeotropic mixed refrigerant such as R407C circulates through the refrigerant circuit (12) while a surplus is stored in a storage part (43) such as a high-pressure receiver.
  • the inside of the storage section (43) is at a high pressure, exists mostly in the state of a liquid refrigerant, and has a smaller amount of gas than liquid.
  • the gas density in the storage part (43) is much smaller than the liquid density. From the above, even if R32 is slightly gasified, the liquid refrigerant stored in the storage part (43) has a composition ratio of the high-boiling refrigerant and the low-boiling refrigerant of the non-azeotropic mixed refrigerant. This state is almost the same as the original composition ratio, and since this liquid refrigerant flows out of the storage part (43), the refrigerant having a stable composition ratio circulates in the refrigerant circuit (1).
  • the direction of circulation of the refrigerant is configured to be reversible, a direction control circuit (41) is provided upstream of the storage section (43), and an expansion mechanism (EV) is provided downstream, the circulation direction of the refrigerant will be correct.
  • the refrigerant flows from the compressor (21) to the condenser (23, 31), the directional control circuit (41), the reservoir (43), the expansion mechanism (EV), and the evaporator (31, 31). 23) goes through the circulation back to the compressor (21) A refrigeration cycle is performed. At that time, the liquid refrigerant flows out while the excess refrigerant is stored in the high-pressure storage section (43), so that the refrigerant having a stable composition ratio also circulates in the circuit (12).
  • liquid seal prevention passage (27) when the operation of the compressor (21) is stopped, even if the refrigerant accumulated in the reservoir (43) expands due to an increase in the ambient temperature, the refrigerant expands. The refrigerant escapes from the discharge pipe side of the compressor (21) to the heat exchanger (23, 31) through the liquid seal prevention passage (27).
  • the non-azeotropic mixed refrigerant such as R407C circulates in the refrigerant circuit (12) in a stable state that hardly changes from the original composition ratio, and the change in the refrigerant characteristics hardly occurs. Therefore, the refrigeration system (10) can exhibit its original capacity stably. Therefore, a decrease in operating efficiency is suppressed, and the reliability of the refrigeration system (10) can be improved. For this reason, the provision of the storage section (43) in the high-pressure liquid line and the configuration in which the accumulator is not used on the suction side of the compressor (21) require a refrigerant circuit (12) using a non-azeotropic mixed refrigerant. Can be said to be extremely suitable for
  • the direction of circulation of the refrigerant in the refrigerant circuit (12) is configured to be reversible, for example, in an air conditioner using a non-azeotropic mixed refrigerant, when performing a cooling operation and performing a heating operation. In either case, stable operation can be achieved.
  • the provision of the liquid seal prevention passage (27) also prevents an abnormal pressure rise around the storage part (43) due to the expansion of the liquid refrigerant accumulated in the storage part (43). Can be prevented.
  • Adjusting the opening of the expansion mechanism (EV) using each temperature sensor (Td, Tc, Te) can further stabilize the composition of the refrigerant, further improving the reliability of the device. It becomes Kakura. BRIEF DESCRIPTION OF THE FIGURES
  • FIG. 1 is a refrigerant circuit diagram of an air conditioner according to an embodiment of the present invention.
  • FIG. 2 is a schematic diagram showing an accumulator in a conventional refrigeration system. BEST MODE FOR CARRYING OUT THE INVENTION
  • the refrigerating apparatus (10) of the present embodiment is a so-called separate type air conditioner (10) in which one indoor unit (30) is connected to one outdoor unit (20).
  • the refrigerant circuit (12) of the air conditioner (10) is configured to perform a vapor compression refrigeration cycle using non-azeotropic mixed refrigerant R407C.
  • the outdoor unit (20) consists of a compressor (21), a four-way switching valve (switching mechanism) (22), an outdoor heat exchanger (23), an auxiliary heat exchanger (24), and an expansion circuit (40). It constitutes a single heat source unit.
  • the indoor unit (30) includes an indoor heat exchanger (31) and constitutes a single utilization unit.
  • the difference between the outdoor heat exchanger (23) and the auxiliary heat exchanger (24) and the indoor heat exchanger (31) is the same as the liquid line (1L) including the expansion circuit (40).
  • the compressor (21) is of, for example, a scroll type in which the operating frequency (operating capacity) is variably adjusted by inversion.
  • a muffler (25) for reducing the operation noise of the compressor (21) is connected to the discharge side of the compressor (21).
  • the silencer (25) has a check valve function that allows only the flow of the refrigerant in the direction from the compressor (21) to the four-way switching valve (22).
  • the four-way switching valve (22) switches during cooling operation as shown by the solid line in FIG. At the time of rotation, the refrigerant is switched as shown by the broken line in FIG. 1 to reverse the circulation direction of the refrigerant in the refrigerant circuit (12).
  • the outdoor heat exchanger (23) and the auxiliary heat exchanger (24) are heat source side heat exchangers that function as a condenser during the cooling operation and function as an evaporator during the heating operation.
  • An outdoor fan (Fo) is provided.
  • the indoor heat exchanger (31) is a use side heat exchanger that functions as an evaporator during the cooling operation and functions as a condenser during the heating operation, and an indoor fan (Fr) is provided near the use side heat exchanger. .
  • the expansion circuit (40) is configured to reduce the pressure of the refrigerant.
  • the expansion circuit (40) includes a direction control circuit (41) composed of a bridge circuit, and a one-way passage (42) connected to the direction control circuit (41).
  • the directional control circuit (41) passes the liquid refrigerant from the heat exchangers (23, 24), (31), which function as condensers, in either one of the cooling operation and the heating operation, in one direction. It is configured to guide to (42).
  • the one-way passage (42) has a receiver (reservoir) (43) that is located upstream and discharges the liquid refrigerant while storing the refrigerant, and an electronic expansion valve that is located downstream and that can be freely opened.
  • (Expansion mechanism) (EV) are arranged in series. With the above configuration, the receiver (43) is always located in the high-pressure liquid line upstream of the electronic expansion valve (EV), and regardless of the refrigerant circulation direction, the condensers (23, 24), (31) ) Flows from the high-pressure liquid refrigerant.
  • a filter (26) for removing dust in the refrigerant is arranged between the receiver (43) and the electronic expansion valve (EV).
  • the direction control circuit (41) includes a first inflow path (44), a first outflow path (45), a second inflow path (46), and a second outflow path (47) in a ridge shape. It is configured to be connected to.
  • Each inflow channel (44, 46) and each outflow channel (45, 47) are provided with check valves (CV, CV, one).
  • the first inflow path (44) is connected from the first connection point (P1) to which the outdoor heat exchanger (23) is connected to a second connection point (P2) to which the upstream end of the one-way passage (42) is connected. To the refrigerant flow.
  • first outflow passage (45) is connected to a third connection point (P3) to which the downstream end of the one-way passage (42) is connected, and to a fourth connection to which the indoor heat exchanger (31) is connected.
  • the refrigerant flows toward point (P4).
  • the second inflow path (46) forms a refrigerant flow from the fourth connection point (P4) to the second connection point (P2).
  • the second outflow channel (47) extends from the third connection point (P3) to the first connection point (P1). Forming a refrigerant flow.
  • the one-way passage (42) is connected to a liquid pipe (high pressure) between the receiver (43) and the electronic expansion valve (EV) (more specifically, between the filter (26) and the electronic expansion valve (EV)).
  • the liquid line is connected to a discharge pipe of the compressor (21) via a liquid seal prevention passage (27) for preventing liquid seal when the compressor (21) is stopped.
  • the liquid seal prevention passage (27) is a one-way passage that allows the refrigerant to flow from the liquid pipe side to the discharge pipe side, and includes a check valve (CV) in the path.
  • a bypass passage (49) is provided between the upper part of the receiver (43) and the downstream side of the electronic expansion valve (EV) in the one-way passage (42) (this part is always a low-pressure liquid line). It is connected. An electromagnetic valve (SV) is provided in the bypass passage (49) so that the gas refrigerant in the receiver (43) can be discharged.
  • SV electromagnetic valve
  • the discharge pipe of the compressor (21) is provided with a discharge pipe temperature sensor (Td) for detecting the discharge pipe temperature of the compressor (21).
  • An outdoor air temperature sensor (Ta) that detects the outdoor air temperature is placed at the air suction port of the outdoor unit (20).
  • the outdoor heat exchanger (23) has a condensing temperature during cooling operation, and has a condensing temperature during heating operation.
  • An outdoor heat exchanger temperature sensor (Tc) for detecting the outdoor heat exchanger temperature, which is the evaporation temperature, is provided.
  • a room temperature sensor (Tr) for detecting the indoor air temperature is arranged at an air suction port of the indoor unit (30), and the indoor heat exchanger (31) has a steam temperature during a cooling operation, and has a heating temperature.
  • An indoor heat exchanger temperature sensor (Te) that detects the temperature of the indoor heat exchanger that becomes the condensing temperature during operation is provided.
  • a high-pressure protection pressure switch that detects a high-pressure refrigerant pressure and is turned on when a high-pressure refrigerant pressure is excessively increased to output a high-pressure protection signal is disposed.
  • a low-pressure protection pressure switch (LSI) that detects a low-pressure refrigerant pressure and turns on when a low-pressure refrigerant pressure is excessively low to output a low-pressure protection signal is provided in the suction pipe of the compressor (21).
  • a low pressure control pressure switch that detects a refrigerant pressure and turns on when the low pressure refrigerant pressure reaches a predetermined value to output a low pressure control signal is disposed.
  • the controller (50) is configured to control each device to perform a cooling operation and a heating operation, and to perform control to stabilize the composition of the non-azeotropic mixed refrigerant flowing in the refrigerant circuit (12). ing.
  • the controller (50) for example, divides the operating frequency of the compressor (21) into the predetermined number of frequency steps N and sets the frequency step N so that the room temperature becomes the set temperature. Control.
  • this controller (50) optimizes the discharge pipe temperature that gives the optimal refrigeration effect from the condensation temperature and evaporation temperature detected by the outdoor heat exchanger temperature sensor (Tc) and the indoor heat exchanger temperature sensor (Te). The value is calculated, and the opening of the electronic expansion valve (EV) is controlled by setting the valve opening so that the discharge pipe temperature becomes the optimum value.
  • the refrigerant circuit (12) of the present embodiment is a circuit that does not use an accumulator on the suction side of the compressor (21) as described above. For this reason, the compressor is controlled by controlling the degree of superheat of the refrigerant sucked into the compressor (21) to be sufficiently large, or by adjusting the outflow of the liquid refrigerant from the receiver (43). Liquid back to (21) is prevented.
  • the gas refrigerant discharged from the compressor (21) is condensed and liquefied in the outdoor heat exchanger (23) and the auxiliary heat exchanger (24), and the liquid refrigerant is supplied to the first inflow path ( After passing through 44), it is temporarily stored in the receiver (43). Then, the liquid refrigerant flows out of the receiver (43), is decompressed by the electronic expansion valve (EV), and then evaporates in the indoor heat exchanger (31) through the first outflow passage (45) to the compressor (21).
  • EV electronic expansion valve
  • the gas refrigerant discharged from the compressor (21) is condensed and liquefied in the indoor heat exchanger (31), and the liquid refrigerant passes through the second inflow passage (46) and is passed through the receiver (43). ) Once stored It is. Then, the liquid refrigerant flows out of the receiver (43) and is decompressed by the electronic expansion valve (EV), and then evaporates in the auxiliary heat exchanger (24) and the outdoor heat exchanger (23) through the second outflow passage (47). And return to the compressor (21). At this time, the circulation operation of the refrigerant is performed while the surplus refrigerant is stored in the receiver (43).
  • the solenoid valve (SV) In both the cooling operation and the heating operation, the solenoid valve (SV) is normally closed so that the gas refrigerant does not flow out of the receiver (43).
  • the pressure inside the receiver (43) is high, and even if R32 gas refrigerant is generated due to the surrounding conditions, the amount is small, and the gas density is lower than the liquid density. And extremely small. Therefore, the composition of the liquid refrigerant flowing out of the receiver (43) hardly changes from the original composition of the non-azeotropic mixed refrigerant R407C used in this circuit (12).
  • the liquid refrigerant having a stable composition flows out of the receiver (43) and circulates in the circuit (12).
  • the controller (50) sets the frequency step N to an appropriate value to control the capacity of the compressor (21), as well as the outdoor heat exchanger temperature sensor (Tc) and From the condensing temperature and evaporating temperature detected by the indoor heat exchanger temperature sensor (Te), the optimum value of the discharge pipe temperature that gives the optimum cooling effect is obtained, and the valve is opened so that the discharge pipe temperature becomes the optimum value. Set the degree. Then, a pulse signal for obtaining the valve opening is transmitted to the electronic expansion valve (25) to control the opening of the electronic expansion valve (EV), and the air conditioning operation corresponding to the indoor load is performed.
  • the non-azeotropic refrigerant mixture is circulated in the refrigerant circuit (12), the operation on the predetermined Mollier diagram is guaranteed. In this case, the ratio of R32 to R134a can be stabilized.
  • a circuit that does not use an accumulator on the suction side of the compressor (21) is used.
  • control is performed such that the degree of superheating of the refrigerant sucked into the compressor (21) is sufficiently large.
  • the accumulator since the accumulator is not used, the composition ratio of the refrigerant does not fluctuate due to the stagnation of the refrigerant on the suction side of the compressor (21).
  • the liquid refrigerant in the receiver (43) expands due to an increase in the ambient temperature in a state where the electronic expansion valve (EV) and the solenoid valve (SV) are closed when the operation is stopped.
  • the coolant flows from the one-way passage (42) through the liquid seal prevention passage (27) and escapes to the heat exchanger (23, 31) side. That is, liquid sealing is prevented.
  • the non-azeotropic mixed refrigerant R 407 C used is a high-pressure receiver (43).
  • the excess amount is stored in the parentheses) to circulate through the refrigerant circuit (12) while adjusting the circulation amount.
  • the pressure inside the receiver (43) is high, most of the liquid exists in the state of liquid refrigerant, and since the density of gas is much smaller than the density of liquid, R32 is gasified.
  • the liquid refrigerant stored in the receiver (43) has a composition ratio that is almost the same as the original composition ratio of R407C.
  • the refrigerant having such a stable composition ratio circulates in the circuit (12), and the composition ratio does not fluctuate on the suction side of the compressor (21).
  • the harmony device (10) can exhibit its original ability stably. Therefore, a decrease in operation efficiency is suppressed, and the reliability of the device (10) can be improved.
  • the refrigerant in the receiver (43) has a high pressure. This is corrected to a state close to the original composition ratio. Therefore, it is possible to reliably prevent the composition ratio of R 407 C from greatly fluctuating during operation.
  • liquid seal prevention passage (27) is provided, even if the ambient temperature rises when the operation is stopped, it is possible to prevent the pressure from rising abnormally.
  • the present invention may be configured as follows in the above embodiment.
  • one indoor unit (30) is connected to one outdoor unit (20), but a plurality of indoor units (20) are connected to one outdoor unit (20). 30) may be connected.
  • the refrigeration apparatus of the present invention is configured as an air conditioner capable of performing a heating operation and a cooling operation.
  • the present invention provides an air conditioner that performs only a heating operation or only a cooling operation.
  • the present invention is also applicable to refrigeration systems other than air conditioners.
  • the refrigerant to be used is not limited to R407C, and other non-azeotropic mixed refrigerants can be used.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

La présente invention concerne un dispositif de réfrigération comprenant un circuit frigorifique (12) prévu pour effectuer un cycle frigorifique du type à compression de vapeur au moyen d'un frigorigène mixte non azéotrope. Dans ce dispositif, une unité (43) de stockage située dans une conduite de liquide haute pression, permet à un frigorigène liquide de s'écouler tout en conservant ce dernier et le côté de sortie d'un évaporateur (31, 23) est connecté au côté aspiration d'un compresseur (21) sans passer par l'intermédiaire d'un accumulateur, la composition d'un frigorigène mixte non azéotrope s'écoulant dans le circuit frigorifique (12) étant ainsi stabilisée ce qui maintient la fiabilité du dispositif (10) de réfrigération et l'empêche de subir une réduction.
PCT/JP2000/008279 1999-11-26 2000-11-24 Dispositif de refrigeration WO2001038801A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP00977900A EP1235043A1 (fr) 1999-11-26 2000-11-24 Dispositif de refrigeration
AU15503/01A AU1550301A (en) 1999-11-26 2000-11-24 Refrigerating device
KR1020027006628A KR20020070982A (ko) 1999-11-26 2000-11-24 냉동 장치

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP33550999A JP2001153480A (ja) 1999-11-26 1999-11-26 冷凍装置
JP11/335509 1999-11-26

Publications (1)

Publication Number Publication Date
WO2001038801A1 true WO2001038801A1 (fr) 2001-05-31

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Application Number Title Priority Date Filing Date
PCT/JP2000/008279 WO2001038801A1 (fr) 1999-11-26 2000-11-24 Dispositif de refrigeration

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EP (1) EP1235043A1 (fr)
JP (1) JP2001153480A (fr)
KR (1) KR20020070982A (fr)
CN (2) CN1141539C (fr)
AU (1) AU1550301A (fr)
WO (1) WO2001038801A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111279141B (zh) * 2017-10-26 2021-06-25 三菱电机株式会社 制冷空调装置以及控制装置
US11250977B2 (en) * 2018-04-09 2022-02-15 Mitsubishi Electric Corporation Superconducting magnet apparatus

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57198968A (en) * 1981-05-29 1982-12-06 Hitachi Ltd Heat pump type refrigerator
JPS6155562A (ja) * 1984-08-24 1986-03-20 ダイキン工業株式会社 混合冷媒を用いた冷凍装置
JPS63153367A (ja) * 1987-12-07 1988-06-25 松下電器産業株式会社 熱ポンプ装置
JPH07103622A (ja) * 1993-09-30 1995-04-18 Toshiba Corp 空気調和機
US5533351A (en) * 1992-11-20 1996-07-09 Daikin Industries, Ltd. Air conditioner

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57198968A (en) * 1981-05-29 1982-12-06 Hitachi Ltd Heat pump type refrigerator
JPS6155562A (ja) * 1984-08-24 1986-03-20 ダイキン工業株式会社 混合冷媒を用いた冷凍装置
JPS63153367A (ja) * 1987-12-07 1988-06-25 松下電器産業株式会社 熱ポンプ装置
US5533351A (en) * 1992-11-20 1996-07-09 Daikin Industries, Ltd. Air conditioner
JPH07103622A (ja) * 1993-09-30 1995-04-18 Toshiba Corp 空気調和機

Also Published As

Publication number Publication date
EP1235043A1 (fr) 2002-08-28
AU1550301A (en) 2001-06-04
CN1298082A (zh) 2001-06-06
CN2458570Y (zh) 2001-11-07
CN1141539C (zh) 2004-03-10
JP2001153480A (ja) 2001-06-08
KR20020070982A (ko) 2002-09-11

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