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WO1998009118A1 - Conditionneur d'air - Google Patents

Conditionneur d'air Download PDF

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Publication number
WO1998009118A1
WO1998009118A1 PCT/JP1997/002746 JP9702746W WO9809118A1 WO 1998009118 A1 WO1998009118 A1 WO 1998009118A1 JP 9702746 W JP9702746 W JP 9702746W WO 9809118 A1 WO9809118 A1 WO 9809118A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
temperature
bypass
heat exchanger
air conditioner
Prior art date
Application number
PCT/JP1997/002746
Other languages
English (en)
Japanese (ja)
Inventor
Koichi Kita
Nobuo Domyo
Kazuyuki Nishikawa
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 AU37833/97A priority Critical patent/AU3783397A/en
Publication of WO1998009118A1 publication Critical patent/WO1998009118A1/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
    • 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
    • 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

Definitions

  • the present invention relates to an air conditioner. More specifically, the present invention relates to an air conditioner including a refrigerant circuit that performs heat exchange between a mainstream refrigerant and a bypass refrigerant to supercool the mainstream refrigerant.
  • the refrigerant circuit 310 of this type of air conditioner includes a compressor 302, a condenser 303, a double-tube heat exchanger 310 for supercooling, Sub-cooling heat exchange with the main circuit 300 having the main expansion mechanism 304, evaporator 305, four-way switching valve 309 and accumulator 308 in this order, and the condenser 303
  • the branch point 3 41 between the heat exchanger 310 and the main circuit 300 passes through the bypass expansion mechanism 3 12 and the subcooling heat exchanger 310, and passes through the accumulator 3 08
  • a bypass circuit (indicated by a broken line) 3 13 that merges with a main circuit 303 at a junction 3 42 near the entrance is known.
  • a single refrigerant such as HCFC (Hide Port Fluorocarbon) 22 is used.
  • HCFC Hydrophilic Fluid
  • the main expansion mechanism 304 a variable throttle made of an electric expansion valve is adopted, while as the bypass expansion mechanism 310, a fixed throttle made of a cable tube is adopted from the viewpoint of cost reduction.
  • the refrigerant discharged from the compressor 302 is condensed by the condenser (for example, radiates heat to the outdoor air) 303, and the mainstream refrigerant flowing in the main circuit 310 at the branch point 341 and the bypass circuit 3 It is divided into the bypass refrigerant flowing through 13.
  • the refrigeration effect of the mainstream refrigerant can be increased as compared with a case where supercooling is not performed.
  • the volume flow rate of the mainstream refrigerant is reduced, as shown in the pressure-specific enthalpy diagram (hereinafter referred to as the “Ph diagram”) in FIG. 11B. It is possible to reduce the pressure loss ⁇ in the evaporator 3005 and the suction side piping of the compressor 302 (for comparison, the pressure loss ⁇ 0 without supercooling is shown in Fig. 11). It is shown in A.). Therefore, the refrigeration capacity of the system can be improved.
  • FIG. 11B which is a partially enlarged view of FIG. 11B, the bypass refrigerant reaching point A and the mainstream refrigerant reaching point B merge to obtain the state at point C.
  • FIG. 11C which is a partially enlarged view of FIG. 11B, the bypass refrigerant reaching point A and the mainstream refrigerant reaching point B merge to obtain the state at point C.
  • the flow rates of the mainstream refrigerant and the bypass refrigerant have been adjusted by changing the throttle amount of an electric expansion valve constituting the main expansion mechanism 304.
  • an electric expansion valve constituting the main expansion mechanism 304.
  • Set the target temperature T d (target) f (T e, T c) at the machine outlet.
  • a temperature sensor at the compressor outlet (discharge pipe) is controlled by control means (not shown).
  • the throttle amount of the main expansion mechanism 304 is adjusted so that the actual discharge pipe temperature Td detected by the filter 31 becomes the target temperature Td (target).
  • the amount of throttle of the capillary tube that constitutes the bypass expansion mechanism 312 depends on the condition that the outdoor temperature is 35 ° C and the indoor temperature is 27 ° C. (Hereinafter referred to as “cooling standard conditions.” Throughout this specification, temperature means dry-bulb temperature (DB) unless otherwise specified.) Refrigeration capacity (coefficient of performance COP) is set under maximum. Have been. That is, when the mainstream refrigerant is saturated at the outlet of the evaporator 305 under the standard cooling condition, the bypass refrigerant is saturated at the bypass-side outlet of the subcooling heat exchanger 310. like
  • an object of the present invention is to provide an air conditioner having a refrigerant circuit for supercooling the mainstream refrigerant by performing heat exchange between the mainstream refrigerant and the bypass refrigerant, under low outside air conditions, particularly under assumed extreme conditions. It is an object of the present invention to provide an air conditioner that can maintain the reliability of a compressor even if it does. Also, an object of the present invention is to provide an air conditioner having a refrigerant circuit for performing heat exchange between a mainstream refrigerant and a bypass refrigerant to supercool the mainstream refrigerant, wherein an electric motor is provided as an expansion mechanism for the bypass refrigerant. It is an object of the present invention to provide an air conditioner that employs a variable throttle composed of an expansion valve and can maintain a high refrigeration capacity regardless of operating conditions.
  • an air conditioner of the present invention comprises: a main circuit for flowing a refrigerant in order of a compressor, a condenser, a supercooling heat exchanger, a first expansion mechanism, and an evaporator;
  • the refrigerant flows from the main circuit branched from the main circuit to the first expansion mechanism to form a second expansion mechanism, a capillary tube, and the supercooling heat exchanger.
  • the above capillary tube has an outdoor temperature lower than the cooling standard condition and an indoor temperature higher than the assumed extreme condition.
  • the discharge of the compressor It is characterized in that a throttle amount such that the pipe temperature becomes equal to or higher than a predetermined lower limit value is given to the bypass-flow refrigerant.
  • the discharge tube temperature of the compressor becomes equal to or higher than a predetermined lower limit under the assumed extreme conditions in which the outdoor temperature is lower than the standard cooling condition and the indoor temperature is higher than the standard cooling condition.
  • a throttle amount is given to the bypass flow refrigerant.
  • the lower limit value of the discharge pipe temperature a value that can maintain the reliability of the compressor (for example, 48 ° C) is set.
  • the amount of throttle of the capillary tube specifically, the dimensions of the capillary tube, is set so that the discharge pipe temperature of the compressor becomes equal to or higher than the value under the assumed extreme conditions. In such a case, even under low outside air conditions, especially under extreme conditions, The discharge pipe temperature of the machine is kept above that value. Therefore, the reliability of the compressor is not impaired, and the reliability is maintained.
  • the size of the capillary tube is such that the mainstream refrigerant is saturated at the outlet of the evaporator under the standard cooling condition.
  • the degree of superheat of the bypass-flow refrigerant at the bypass side outlet of the supercooling heat exchanger is set to be 4.5 deg or more.
  • the present inventor has conducted experiments, as shown in FIG. 2, when the discharge pipe temperature of the compressor under the assumed extreme conditions is such that the mainstream refrigerant is saturated at the outlet of the evaporator under standard cooling conditions. However, it was confirmed that it corresponded to the degree of superheat of the bypass-flow refrigerant passing through the bypass-side outlet of the supercooling heat exchanger ( ⁇ in Fig. 2 indicates data points). Therefore, in the air conditioner of this embodiment, the size (that is, the diameter and the length) of the cavity tube is adjusted when the mainstream refrigerant is saturated at the outlet of the evaporator under the standard cooling condition. Set the degree of superheat of the bypass flow refrigerant at the bypass side outlet of the cooling heat exchanger to be 4.5 deg or more.
  • the discharge pipe temperature of the compressor under low outside air conditions becomes 48 C or higher at which the reliability of the compressor can be maintained. Therefore, the reliability of the compressor is not impaired, and the reliability is maintained. Also, since only the dimensions of the capillary tube are set, the cost is not higher than in the past.
  • the superheat degree of the bypass-flow refrigerant at the bypass side outlet of the supercooling heat exchanger under the cooling standard condition is set to zero (saturated state).
  • the discharge pipe temperature of the compressor is about 46 ° C.
  • a compressor, a condenser, and a heat exchanger for supercooling are used.
  • a refrigerant circuit including a billet tube and a bypass circuit for flowing the refrigerant in the order of the supercooling heat exchanger and merging with the main circuit on the suction side of the compressor, wherein the supercooling heat exchanger includes: An air conditioner that performs heat exchange between a mainstream refrigerant flowing through the main circuit and a bypass flow refrigerant flowing through the bypass circuit after passing through the capillary tube to supercool the mainstream refrigerant.
  • a refrigerant shut-off mechanism that can shut off the refrigerant is provided.
  • the amount of throttling that the capillary tube gives to the bypass flow refrigerant is such that when the main flow refrigerant becomes saturated at the outlet of the evaporator under the cooling standard conditions, the supercooling heat exchange is performed.
  • the bypass refrigerant at the bypass-side outlet of the vessel may be preset to be saturated.
  • the refrigerant shut-off mechanism is opened and the bypass refrigerant flows through the bypass circuit. Is distributed.
  • the refrigerant shut-off mechanism includes the main circuit And a subcooling heat exchanger.
  • the refrigerant shutoff mechanism is interposed between the branch from the main circuit and the supercooling heat exchanger, the pressure loss caused by the refrigerant shutoff mechanism is It works in the direction of reducing the pressure at the bypass-side inlet of the industrial heat exchanger and lowering this temperature. Therefore, the amount of heat exchange in the supercooling heat exchanger does not decrease due to the presence of the refrigerant shut-off mechanism.
  • the refrigerant shut-off mechanism is arranged downstream of the supercooling heat exchanger, the pressure at the bypass-side inlet of the supercooling heat exchanger rises by the pressure loss at the refrigerant shut-off mechanism, and the temperature there is increased. Rises. For this reason, the amount of heat exchange in the subcooling heat exchanger decreases.
  • the outdoor temperature (To) and the indoor temperature (Tr) are detected by the temperature sensor, and whether the detected outdoor temperature (To) and the indoor temperature (Tr) satisfy predetermined conditions is determined. And opening and closing the refrigerant shut-off mechanism based on the pressure.
  • the refrigerant shut-off mechanism is opened and closed based on whether the outdoor temperature (To) and the indoor temperature (Tr) satisfy predetermined conditions, so that the refrigerant shut-off mechanism is accurately controlled.
  • a temperature sensor for detecting the outdoor temperature (To) and a temperature sensor for detecting the indoor temperature (Tr) are generally provided in an air conditioner, so a special new temperature sensor is required. No need to add.
  • the refrigerant shut-off mechanism is closed when the difference (To—Tr) between the detected outdoor temperature and the indoor temperature is equal to or less than ⁇ 15 deg during operation. On the other hand, when this condition is not satisfied, the refrigerant shut-off mechanism is opened.
  • FIG. 5B the inventor has determined that the outdoor air temperature (To) and the indoor air temperature (Tr)
  • Fig. 5A the outdoor air temperature and the indoor air temperature It has been confirmed that there is a certain relationship between the difference (To-Tr) between the temperature and the degree of superheat of the refrigerant passing through the discharge pipe of the compressor (the difference between the discharge pipe temperature and the saturation temperature corresponding to the discharge side pressure) (The squares in Figure 5A indicate data points).
  • FIG. 5B each marked with one to four
  • the refrigerant shutoff mechanism is accurately controlled, and the reliability of the compressor is maintained.
  • the outlet temperature (Tc) of the condenser and the inlet temperature (Te) of the evaporator are detected by a temperature sensor, and the detected outlet temperature (Tc) and the detected outlet temperature of the condenser are detected.
  • the refrigerant shut-off mechanism is opened and closed based on whether the inlet temperature (Te) of the evaporator satisfies a predetermined condition.
  • the refrigerant shut-off mechanism is opened and closed based on whether or not the outlet temperature (Tc) of the condenser and the inlet temperature (Te) of the evaporator satisfy predetermined conditions. Is precisely controlled, and compressor reliability is maintained.
  • An air conditioner includes a main circuit for flowing a refrigerant in order of a compressor, a condenser, a supercooling heat exchanger, a first expansion mechanism, and an evaporator; A bypass circuit branching off from the main circuit between the main circuit and a second expansion mechanism, a refrigerant flowing in the order of the supercooling heat exchanger, and a merging with the main circuit on the suction side of the compressor.
  • the subcooling heat exchanger exchanges heat between the mainstream refrigerant flowing through the main circuit and a bypass refrigerant flowing through the bypass circuit after passing through the second expansion mechanism.
  • the second expansion mechanism is configured by combining two or more capillary tubes and at least one refrigerant shutoff mechanism capable of shutting off the refrigerant in a predetermined arrangement.
  • a throttle provided to the bypass flow refrigerant It is possible to set the amount in a plurality of steps.
  • the throttle amount given to the bypass-flow refrigerant by the second expansion mechanism is set to a relatively small stage under the standard cooling condition or overload condition.
  • the amount of throttling applied to the bypass flow refrigerant by the second expansion mechanism is such that the main flow refrigerant becomes saturated at the outlet of the evaporator under the cooling standard conditions.
  • the bypass refrigerant at the bypass-side outlet of the subcooling heat exchanger is set to be saturated.
  • the throttle amount given to the bypass-flow refrigerant by the second expansion mechanism is set to a relatively large stage.
  • the second expansion mechanism is completely closed and the flow of the bypass refrigerant is cut off.
  • the bypass refrigerant does not merge with the mainstream refrigerant and flow into the compressor in a state of high wetness. Therefore, the reliability of the compressor is not impaired, and the reliability is maintained.
  • the second expansion mechanism is set at a stage where the throttle amount is relatively large, or the second expansion mechanism is There is no problem if the is completely closed.
  • the air conditioner of another embodiment detects the outdoor temperature (To) and the indoor temperature (Tr) by using the temperature sensor, and determines whether the detected outdoor temperature (To) and the indoor temperature (Tr) satisfy predetermined conditions.
  • the stage of the throttle amount of the second expansion mechanism is set based on whether or not.
  • the stage of the throttle amount of the second expansion mechanism is set based on whether or not the outdoor temperature (To) and the indoor temperature (Tr) satisfy predetermined conditions.
  • the expansion mechanism is precisely controlled.
  • the air conditioner of another embodiment detects the outlet temperature (Tc) of the condenser and the inlet temperature (Te) of the evaporator with a temperature sensor, and detects the detected outlet temperature (Tc) of the condenser. Further, the stage of the throttle amount of the second expansion mechanism is determined based on whether or not the inlet temperature (Te) of the evaporator satisfies a predetermined condition.
  • An air conditioner includes a main circuit for flowing a refrigerant in order of a compressor, a condenser, a supercooling heat exchanger, a first expansion mechanism, and an evaporator; A bypass circuit branching off from the main circuit between the main circuit and a second expansion mechanism, a refrigerant flowing in the order of the supercooling heat exchanger, and a merging with the main circuit on the suction side of the compressor.
  • the subcooling heat exchanger comprises: a mainstream refrigerant flowing through the main circuit; and the bypass pipe after passing through the second expansion mechanism.
  • the first expansion mechanism is a first electric expansion valve
  • the second expansion mechanism is a second expansion mechanism. The first and second electric expansion valves respectively control the degree of superheat at the outlet of the evaporator and the degree of superheat at the bypass side outlet of the subcooling heat exchanger. .
  • the first expansion mechanism is constituted by a first electric expansion valve
  • the second expansion mechanism is constituted by a second electric expansion valve
  • the first and second electric expansion valves are used for the first expansion mechanism. Since the degree of superheat at the outlet of the evaporator and the degree of superheat at the outlet on the bypass side of the supercooling heat exchanger are controlled, finer and more precise control is possible. Therefore, the advantage of supercooling can be fully utilized, and high refrigeration capacity can be maintained regardless of operating conditions.
  • the refrigeration capacity of the refrigerant circuit is maximized when the superheat degree of the mainstream refrigerant passing through the outlet of the evaporator is zero (saturated) and passing through the bypass-side outlet of the supercooling heat exchanger.
  • the degree of superheat of the bypass-flow refrigerant is zero (saturated state)
  • the state of the refrigerant passing through each outlet varies from the saturated state to the wet side
  • the reliability of the compressor may be impaired. Therefore, by controlling the degree of superheat of the refrigerant at each of the outlets, the state of the refrigerant is adjusted from the saturated state to a slightly superheated side. As a result, the reliability of the compressor is maintained.
  • the pressure (P s) on the suction side of the compressor is detected by a pressure sensor, and the saturation temperature (T s) of the refrigerant corresponding to this pressure is calculated.
  • the temperature sensor detects the outlet temperature of the evaporator (T e0) and the outlet temperature of the bypass side of the subcooling heat exchanger (T bo), and detects the outlet temperature of the evaporator and the equivalent saturation temperature.
  • the difference (T eo-T s) is calculated as the degree of superheat of the mainstream refrigerant passing through the outlet of the evaporator, and the difference (T b) between the bypass side outlet temperature of the subcooling heat exchanger and the equivalent saturation temperature is calculated.
  • oT s is calculated as the degree of superheat of the bypass flow coolant passing through the bypass side outlet of the supercooling heat exchanger, and the first superheat degree is calculated so that the calculated superheat degree of the mainstream refrigerant becomes a predetermined target superheat degree.
  • a control unit is provided for controlling the electric expansion valve and for controlling the second electric expansion valve so that the calculated superheat degree of the bypass-flow refrigerant becomes a predetermined target superheat degree.
  • the degree of superheating of the mainstream refrigerant passing through the outlet of the evaporator and the degree of superheating of the bypass flowing refrigerant passing through the bypass-side outlet of the subcooling heat exchanger are accurately controlled.
  • the air conditioner of another embodiment includes the condenser outlet temperature (Tc), the evaporator inlet temperature (Te), the compressor discharge pipe temperature (Td), and the supercooling heat.
  • a main motor-operated valve control unit that controls the first motor-operated expansion valve so that the detected discharge pipe temperature (T d) of the compressor becomes the target temperature (Td (target));
  • the difference between the outlet temperature (Tbo) on the bypass side of the subcooling heat exchanger (Tbo) and the inlet temperature (Tbi) (Tbo-Tbi) Force Controls the second electric expansion valve so that it reaches a predetermined target value
  • a bypass motor-operated valve control unit
  • the superheat degree of the mainstream refrigerant passing through the outlet temperature of the evaporator (Te 0) and the superheat degree of the bypass flow refrigerant passing through the bypass-side outlet temperature (Tbo) of the supercooling heat exchanger is precisely controlled.
  • An air conditioner includes a main circuit for flowing a refrigerant in order of a compressor, a condenser, a supercooling heat exchanger, a first expansion mechanism, and an evaporator; Branch from the main circuit to the second expansion mechanism; A refrigerant circuit including a bypass circuit that flows the refrigerant in the order of the cooling heat exchanger and merges with the main circuit on the suction side of the compressor; the subcooling heat exchanger includes a main flow that flows through the main circuit.
  • the electric expansion valve and the second expansion mechanism are each constituted by an automatic temperature expansion valve, and the electric expansion valve and the automatic temperature expansion valve are used to superheat the outlet of the evaporator and to bypass the supercooling heat exchanger. Controls the degree of superheat at the side outlet.
  • FIG. 1 is a diagram showing a schematic configuration of a refrigerant circuit of an air conditioner according to a first embodiment of the present invention.
  • FIG. 2 is a diagram illustrating a characteristic change when the amount of throttle applied to the bypass flow coolant by the capillary tube in the refrigerant circuit of FIG. 1 is changed.
  • FIG. 3 is a diagram showing a schematic configuration of a refrigerant circuit of an air conditioner according to a second embodiment of the present invention.
  • FIG. 4 is a diagram showing a schematic configuration of a refrigerant circuit of an air conditioner according to a third embodiment of the present invention.
  • FIG. 5A is a diagram showing operating conditions under which the refrigerant circuit of FIG. 3 was experimentally operated, that is, a combination of the outdoor temperature To and the indoor temperature Tr, and FIG. FIG. 3 is a graph showing the relationship between the difference between the outdoor temperature and the indoor temperature (T o ⁇ T r) and the degree of superheat of the discharge pipe.
  • FIG. 6 is a diagram showing a schematic configuration of a refrigerant circuit of an air conditioner according to a fourth embodiment of the present invention.
  • FIG. 7 is a diagram illustrating a schematic configuration of a refrigerant circuit of an air conditioner according to a fifth embodiment of the present invention.
  • FIG. 8 is a diagram illustrating a schematic configuration of a refrigerant circuit of an air conditioner according to a sixth embodiment of the present invention.
  • FIG. 9 is a diagram schematically showing how to calculate a target temperature T d (target) of the discharge pipe of the compressor from the outlet temperature T c of the condenser and the inlet temperature Te of the evaporator.
  • FIG. 10 is a diagram showing a schematic configuration of a refrigerant circuit of a conventional air conditioner that performs heat exchange between a mainstream refrigerant and a bypass refrigerant to supercool the mainstream refrigerant.
  • FIG. 11A is a Ph diagram showing a refrigeration cycle without supercooling
  • FIG. 11B is a Ph diagram showing a refrigeration cycle using the conventional refrigerant circuit shown in FIG. 1C is a partially enlarged view of FIG. 11B.
  • FIG. 1 shows a refrigerant circuit 1 including a main circuit 6 and a bypass circuit (indicated by a broken line) 11 of the air conditioner of the first embodiment.
  • the supercooling heat exchanger 10 exchanges heat between the mainstream refrigerant flowing through the main circuit 6 and the bypass refrigerant flowing through the bypass circuit 11 after passing through the capillary tube 12. That is, the bypass refrigerant flowing through the capillary tube 12 is used to supercool the mainstream refrigerant with a simple circuit configuration.
  • the refrigerant discharged from the compressor 2 is condensed by a condenser (for example, radiates heat to outdoor air) 3, and flows into the main circuit 6 at the branch point 4 1 and the bypass refrigerant flowing through the bypass circuit 11. And break up.
  • This mainstream refrigerant is supercooled by heat exchange with the bypass-flow refrigerant after passing through the capillary tube 12 in the heat exchanger 10, and then decompressed by the electric expansion valve 4.
  • the mainstream refrigerant is evaporated by an evaporator (for example, absorbing heat from indoor air) 5, and is sucked into the compressor 2 through a four-way switching valve 9 and an accumulator 8 for performing gas-liquid separation.
  • bypass flow refrigerant is depressurized by passing through the capillary tube 12 giving a predetermined throttle amount, and is then evaporated in the heat exchanger 10 by heat exchange with the main flow refrigerant. Thereafter, the bypass-flow refrigerant merges with the mainstream refrigerant at a junction 42 near the inlet of the accumulator 8.
  • the dimensions (ie, diameter and length) of the capillary tube 12 are determined by the evaporator under standard cooling conditions (outdoor temperature of 35 ° C and indoor temperature of 27 ° C). Subcooling heat exchanger when mainstream refrigerant is saturated at outlet 5
  • the superheat degree of the bypass-flow refrigerant at the bypass-side outlet of 10 is set to be 4.5 deg or more.
  • the discharge pipe temperature T d of the compressor 2 under (28 ° C. in (WB)) becomes 48 ° C. or more at which the reliability of the compressor 2 can be maintained. Therefore, it is possible to prevent the reliability of the compressor 2 from being impaired, and to maintain the reliability. Ma Further, since only the dimensions of the capillary tube 12 are set, the cost does not increase as compared with the conventional case.
  • FIG. 3 shows a refrigerant circuit 1A including a main circuit 6 and a bypass circuit (shown by a broken line) 11A of the air conditioner of the second embodiment.
  • a refrigerant circuit 1A including a main circuit 6 and a bypass circuit (shown by a broken line) 11A of the air conditioner of the second embodiment.
  • FIG. 3 shows a refrigerant circuit 1A including a main circuit 6 and a bypass circuit (shown by a broken line) 11A of the air conditioner of the second embodiment.
  • FIG. 3 shows a refrigerant circuit 1A including a main circuit 6 and a bypass circuit (shown by a broken line) 11A of the air conditioner of the second embodiment.
  • bypass circuit 11 A is provided between the capillary tube 12 F constituting the second expansion mechanism and the supercooling heat exchanger 10 by an electromagnetic on-off valve 1 serving as a refrigerant shut-off mechanism. Has three.
  • the dimensions of the capillary tube 12F are such that when the mainstream refrigerant is saturated at the outlet of the evaporator 5 under standard cooling conditions, the bypass refrigerant at the bypass side outlet of the supercooling heat exchanger 10 It is set in advance so as to be saturated. That is, the throttle amount given to the bypass-flow refrigerant is set smaller than that of the capillary tube 12 in FIG.
  • the outdoor temperature To and the indoor temperature Tr are detected by the temperature sensor 38 for detecting the outdoor air temperature and the temperature sensor 39 for detecting the indoor air temperature during the cooling operation.
  • the control means (not shown) closes the solenoid on-off valve 13 when the difference between the detected outdoor air temperature and the indoor air temperature (To—T r) satisfies the condition of ⁇ 15 deg or less. Open the solenoid on-off valve 13.
  • ⁇ in FIG. 5A indicates data points
  • the outlet temperature Tc of the condenser 3 and the inlet temperature Te of the evaporator 5 are detected by the temperature sensor 32 at the outlet of the condenser 3 and the temperature sensor 33 at the inlet of the evaporator 5, respectively.
  • the electromagnetic on-off valve 13 may be opened and closed based on whether the outlet temperature Tc and the inlet temperature Te of the evaporator 5 satisfy predetermined conditions. Also in this case, basically, the electromagnetic on-off valve 13 can be opened and closed similarly to the case of using the temperature sensor 38 for detecting the outdoor air temperature and the temperature sensor 39 for detecting the indoor air temperature. can do.
  • the solenoid on-off valve 13 is inserted between the capillary tube 12 F and the supercooling heat exchanger 10, the pressure loss caused by the solenoid on-off valve 13 is It works to lower the pressure at the bypass-side inlet of vessel 10 and to lower the temperature there. Therefore, the amount of heat exchange in the supercooling heat exchanger 10 does not decrease due to the presence of the solenoid on-off valve 13.
  • the solenoid on-off valve 13 only needs to be interposed between the branch point 41 from the main circuit 6 and the supercooling heat exchanger 10, and the branch point 41 and the capillary tube 1 2 It may be inserted between F and.
  • FIG. 4 shows a refrigerant circuit 1B of the air conditioner of the third embodiment including a main circuit 6 and a bypass circuit (shown by a broken line) 11B.
  • a main circuit 6 shows a main circuit 6 and a bypass circuit (shown by a broken line) 11B.
  • a bypass circuit shown by a broken line 11B.
  • components corresponding to those in FIG. 1 will be assigned the same reference numerals, and only differences from the first embodiment will be described.
  • the bypass circuit 11 B is divided into a plurality of shunt circuits 17 A, 17 B,... In parallel between the branch point 41 from the main circuit 6 and the supercooling heat exchanger 10. , 17 C.
  • a shunt tube 12 A is arranged in the shunt circuit 17 A
  • a squirrel tube 12 B and a solenoid on-off valve 13 B are arranged in this order in the shunt circuit 17 B, and so on.
  • a capillary tube 12C and a solenoid on-off valve 13C are arranged in this order.
  • the second expansion mechanism 18 is constituted by the combination of these capillary tubes 12 A, 12 B,..., 12 C and the solenoid on-off valves 13 B,. ing.
  • capillary tubes 12 A, 12 B, ..., 12 ⁇ are respectively connected to the refrigerant flowing through the respective shunt circuits 17 A, 17 B, ..., 17 C.
  • Various dimensions are set to give different amounts of drawing.
  • the solenoid on-off valves 13 B, ' ⁇ , 13 C the second expansion mechanism 18 as a whole is opened and closed.
  • the amount of throttle to be given to the bypass-flow refrigerant can be set in a plurality of stages. Under the cooling standard condition or the overload condition, the throttle amount given to the bypass flow coolant by the second expansion mechanism 18 is set to a relatively small stage.
  • the amount of throttle given to the bypass flow refrigerant by the second expansion mechanism 18 is determined when the main flow refrigerant is saturated at the outlet of the evaporator 5 under the standard cooling condition.
  • the bypass refrigerant at the bypass-side outlet of the subcooling heat exchanger 10 is set to be saturated.
  • the throttle amount given to the bypass-flow refrigerant by the second expansion mechanism 18 is set to a relatively large stage. Thereby, the wetness of the bypass-flow refrigerant after passing through the subcooling heat exchanger 10 decreases.
  • the outdoor temperature T o and the indoor air temperature are detected by the temperature sensor 38 for detecting the outdoor air temperature and the temperature sensor 39 for detecting the indoor air temperature. Detect Tr.
  • the throttle amount of the second expansion mechanism 18 is relatively small. If this condition is not fulfilled while setting to a large stage, the throttle amount of the second expansion mechanism 18 Is set to a relatively small step. As a result, the second expansion mechanism 18 can be accurately controlled, and the reliability of the compressor 2 can be maintained.
  • the outlet temperature Tc of the condenser 3 and the inlet temperature Te of the evaporator 5 are detected by the temperature sensor 32 at the outlet of the condenser 3 and the temperature sensor 33 at the inlet of the evaporator 5, respectively.
  • the stage of the throttle amount of the second expansion mechanism 18 may be set based on whether the outlet temperature Tc of 3 and the inlet temperature Te of the evaporator 5 satisfy predetermined conditions.
  • FIG. 6 shows a refrigerant circuit 1C including a main circuit 6 and a bypass circuit (shown by a broken line) 11C of the air conditioner of the fourth embodiment.
  • a refrigerant circuit 1C including a main circuit 6 and a bypass circuit (shown by a broken line) 11C of the air conditioner of the fourth embodiment.
  • FIG. 6 shows a refrigerant circuit 1C including a main circuit 6 and a bypass circuit (shown by a broken line) 11C of the air conditioner of the fourth embodiment.
  • FIG. 6 shows a refrigerant circuit 1C including a main circuit 6 and a bypass circuit (shown by a broken line) 11C of the air conditioner of the fourth embodiment.
  • the refrigerant circuit 1C includes a first electric expansion valve 4 as a first expansion mechanism, a second electric expansion valve 14 as a second expansion mechanism, and these electric expansion valves.
  • a saturation temperature calculation unit 21, comparison units 22 and 24, a main motorized valve control unit 23, and a bypass motorized valve control unit 25 are provided.
  • the pressure Ps on the suction side of the compressor 2 is detected by the pressure sensor 40 attached to the inlet side of the accumulator 8, and the refrigerant corresponding to the pressure Ps is detected by the saturation temperature calculation unit 21.
  • the equivalent saturation temperature T s of is calculated by the outlet temperature T eo of the evaporator 5 .
  • the difference (T eo-T s) between the outlet temperature T e0 of the evaporator 5 and the equivalent saturation temperature T s is calculated by the comparator 22 as the superheat of the mainstream refrigerant passing through the outlet of the evaporator 5.
  • the main motorized valve control unit 23 controls the electric power so that the calculated superheat degree (T eo-T s) of the mainstream refrigerant becomes a predetermined target superheat degree.
  • the dynamic expansion valve 4 is controlled.
  • the bypass-side outlet temperature (temperature of the bypass-flow refrigerant at the bypass-side outlet) T bo is detected by the temperature sensor 35 at the bypass-side outlet of the subcooling heat exchanger 10.
  • the difference (Tb 0—T s) between the bypass side outlet temperature T bo and the equivalent saturation temperature T s is determined by the comparison unit 24 by the bypass refrigerant flowing through the bypass side outlet of the supercooling heat exchanger 10. Calculate as superheat (T bo-T s).
  • the bypass motor-operated valve control unit 25 controls the motor-operated expansion valve 14 so that the calculated superheat degree (T bo-T s) of the bypass-flow refrigerant becomes the predetermined target superheat degree.
  • the degree of superheat of the mainstream refrigerant passing through the outlet of the evaporator 5 and the degree of superheat of the bypass-flow refrigerant passing through the bypass-side outlet of the supercooling heat exchanger 10 can be accurately controlled. Therefore, the advantage of performing subcooling can be fully utilized, and high refrigeration capacity can be maintained regardless of operating conditions.
  • the refrigeration capacity of the refrigerant circuit 1 is maximized when the superheat degree of the mainstream refrigerant passing through the outlet of the evaporator 5 is zero (saturated) and the bypass side outlet of the supercooling heat exchanger 10 is provided.
  • the degree of superheat of the bypass refrigerant flowing through the outlet is zero (saturated state)
  • the reliability of the compressor 2 may be impaired. Therefore, by controlling the degree of superheat of the refrigerant at each outlet as described above, the state of the refrigerant is adjusted from the saturated state to a somewhat superheated side. Thereby, the reliability of the compressor 2 can be maintained.
  • FIG. 7 shows a refrigerant circuit 1D including a main circuit 6 and a bypass circuit (shown by a broken line) 11D of the air conditioner of the fifth embodiment.
  • a refrigerant circuit 1D including a main circuit 6 and a bypass circuit (shown by a broken line) 11D of the air conditioner of the fifth embodiment.
  • the outlet temperature Tc of the condenser 3 is detected by the temperature sensor 32 at the outlet of the condenser 3, and the inlet temperature Te of the evaporator 5 is detected by the temperature sensor 33 at the inlet of the evaporator 5.
  • the target temperature Td (target) f (Te, Tc) of the compressor outlet as a function f of the outlet temperature Tc of the condenser 3 and the inlet temperature Te of the evaporator 5 by the discharge pipe target temperature calculator 26.
  • the actual discharge pipe temperature Td is detected by the temperature sensor 31 at the outlet (discharge pipe) of the compressor 2.
  • the difference (Td—Td (target)) between the actual discharge pipe temperature Td and the target temperature Td (target) is calculated by the comparing section 27, and the difference (Td—Td (target) is calculated by the main motor-operated valve control section 23. Adjust the throttle amount of the electric expansion valve 4 so that)) becomes zero.
  • the bypass-side outlet temperature Tbo is detected by the temperature sensor 35 at the bypass-side outlet of the subcooling heat exchanger 10
  • the bypass-side temperature is detected by the temperature sensor 34 at the bypass-side inlet of the subcooling heat exchanger 10.
  • Inlet temperature (temperature of the refrigerant flowing through the bypass passing through the bypass side inlet) Tbi is detected.
  • the difference (Tbo-Tbi) between the bypass-side outlet temperature Tb0 and the bypass-side inlet temperature Tbi is calculated by the comparing unit 29, and the difference (Tbo-Tbi) is determined by the bypass-side electric valve control unit 25.
  • the electric expansion valve 14 is controlled so as to reach the target value.
  • the degree of superheat of the mainstream refrigerant passing through the outlet of the evaporator 5 and the degree of superheat of the bypass refrigerant flowing through the bypass-side exit of the supercooling heat exchanger 10 are targeted. It can be controlled exactly. Therefore, the advantage of performing subcooling can be fully utilized, and high refrigeration capacity can be maintained regardless of operating conditions.
  • FIG. 8 shows a refrigerant circuit 1E including a main circuit 6 and a bypass circuit (shown by a broken line) 11E of the air conditioner of the sixth embodiment.
  • a refrigerant circuit 1E including a main circuit 6 and a bypass circuit (shown by a broken line) 11E of the air conditioner of the sixth embodiment.
  • FIG. 8 shows a refrigerant circuit 1E including a main circuit 6 and a bypass circuit (shown by a broken line) 11E of the air conditioner of the sixth embodiment.
  • FIG. 8 shows a refrigerant circuit 1E including a main circuit 6 and a bypass circuit (shown by a broken line) 11E of the air conditioner of the sixth embodiment.
  • the refrigerant circuit 1E includes an electric expansion valve 4 as a first expansion mechanism and an automatic temperature expansion valve 15 as a second expansion mechanism.
  • the temperature automatic expansion valve 15 has a temperature sensing tube 15a, and the opening of the valve is automatically adjusted according to the temperature detected by the temperature sensing tube 15a.
  • the temperature sensing tube 15a is attached to the outlet pipe on the bypass side of the supercooling heat exchanger 10.
  • the temperature-sensitive cylinder 15a detects the bypass-side outlet temperature Tb0 of the subcooling heat exchanger 10 by the temperature sensing cylinder 15a, and the amount of throttle that the automatic temperature expansion valve 15 gives to the bypass-flow refrigerant according to the detection signal. Is controlled.
  • the degree of superheat of the bypass-flow refrigerant passing through the bypass-side outlet temperature Tb0 of the subcooling heat exchanger 10 is automatically controlled by itself. As a result, there is no need to provide any other sensors or control means, and the configuration of the air conditioner can be simplified.
  • the reliability in the case of lack of gas can be improved.
  • the electric expansion valve 304 becomes insufficient in capacity
  • the discharge pipe temperature T d becomes extremely high
  • the protection control is activated to prevent the air from flowing.
  • the harmonic machine may stop abnormally.
  • the main circuit 6 and the bypass circuit 11C.11D or 11E are substantially in parallel. Yes, two When the electric expansion valves 4, 14 (or 15) are combined, the valve capacity becomes larger than that of the conventional refrigerant circuit 301. Therefore, the gas shortage resistance is improved, and the abnormal stop due to the rise in the discharge pipe temperature Td is less likely to occur than in the conventional refrigerant circuit 301. As a result, reliability is improved.
  • the bypass circuit 11 branches from the main circuit between the condenser 3 and the supercooling heat exchanger 10, but the present invention is not limited to this.
  • the bypass circuit branches from the main circuit between the supercooling heat exchanger 10 and the electric expansion valve 4 so that the bypass refrigerant flows in the order of the second expansion mechanism and the supercooling heat exchanger. You may be familiar. In this case, the same operation and effect can be obtained.
  • the present invention is applicable to an air conditioner having a refrigerant circuit for performing supercooling, and is useful for improving the reliability of a compressor of an air conditioner under extreme conditions.

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

Abstract

Un circuit réfrigérant (1) du conditionneur d'air selon la présente invention comporte un circuit principal (6) qui permet à un fluide réfrigérant de couler à travers un compresseur (2), un condensateur (3), un échangeur de chaleur à surfusion (10), un premier mécanisme d'expansion (4) et un évaporateur, dans l'ordre mentionné, et un circuit de dérivation (11) qui part depuis le circuit principal (6) en un point situé entre le condensateur (3) et le mécanisme d'expansion (4), qui permet au réfrigérant de couler à travers un tube capillaire (12) constituant un second mécanisme d'expansion et l'échangeur de chaleur à surfusion (10), dans l'ordre cité, et qui rejoint le circuit principal (6) du côté aspiration du compresseur (2). Le tube capillaire (12) apporte une certaine quantité d'admission à un réfrigérant du flux de dérivation si bien que la température Td de conduit d'évacuation du compresseur (2) est supérieure à une valeur limite inférieure prédéterminée en cas de condition critique hypothétique. Par conséquent, la fiabilité du compresseur peut être assurée, même en cas de condition critique hypothétique dans laquelle la température extérieure est de -5 °C et la température intérieure est de 28 °C (WB).
PCT/JP1997/002746 1996-08-27 1997-08-07 Conditionneur d'air WO1998009118A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU37833/97A AU3783397A (en) 1996-08-27 1997-08-07 Air conditioner

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP22482596A JPH1068553A (ja) 1996-08-27 1996-08-27 空気調和機
JP8/224825 1996-08-27

Publications (1)

Publication Number Publication Date
WO1998009118A1 true WO1998009118A1 (fr) 1998-03-05

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1026460A1 (fr) * 1998-08-21 2000-08-09 Daikin Industries, Limited Echangeur de chaleur du type a double tube et machine frigorifique utilisant cet echangeur de chaleur
JP2002243301A (ja) * 2001-02-14 2002-08-28 Daikin Ind Ltd 熱交換ユニット及び空気調和装置
CN100441964C (zh) * 2005-02-03 2008-12-10 乐金电子(天津)电器有限公司 多级型空调器
CN102032725A (zh) * 2010-12-08 2011-04-27 海尔集团公司 过冷装置、具有该装置的空调、控制空调冷媒流量的方法
CN104114964A (zh) * 2012-11-26 2014-10-22 松下电器产业株式会社 制冷循环装置和具备其的热水生成装置
WO2022099748A1 (fr) * 2020-11-10 2022-05-19 艾默生环境优化技术(苏州)有限公司 Système de pompe à chaleur

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JP3440910B2 (ja) * 2000-02-17 2003-08-25 ダイキン工業株式会社 冷凍装置
JP2003074991A (ja) * 2001-08-31 2003-03-12 Daikin Ind Ltd 冷凍装置
JP4036288B2 (ja) * 2002-07-11 2008-01-23 株式会社日立製作所 空気調和装置
CN1283961C (zh) * 2002-08-02 2006-11-08 大金工业株式会社 冷冻装置
JP2004170048A (ja) * 2002-11-22 2004-06-17 Daikin Ind Ltd 空気調和装置
US20070000262A1 (en) 2005-06-30 2007-01-04 Denso Corporation Ejector cycle system
JP5217121B2 (ja) * 2005-06-30 2013-06-19 株式会社デンソー エジェクタ式冷凍サイクル
JP3894221B1 (ja) * 2005-08-29 2007-03-14 ダイキン工業株式会社 空気調和装置
KR101042472B1 (ko) * 2008-12-30 2011-06-16 세협기계(주) 과부하 제어장치가 설치되는 히트펌프 시스템
JP5533491B2 (ja) * 2010-09-24 2014-06-25 パナソニック株式会社 冷凍サイクル装置及び温水暖房装置
JP5278451B2 (ja) * 2011-01-27 2013-09-04 パナソニック株式会社 冷凍サイクル装置及びそれを用いた温水暖房装置
JP5637053B2 (ja) 2011-04-07 2014-12-10 パナソニック株式会社 冷凍サイクル装置及びそれを備えた温水暖房装置
JP5816789B2 (ja) * 2011-06-17 2015-11-18 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置及びそれを備えた温水暖房装置
JP2013127332A (ja) 2011-12-19 2013-06-27 Panasonic Corp 温水暖房装置
JP6020819B2 (ja) * 2013-03-25 2016-11-02 株式会社富士通ゼネラル 空気調和装置
JP6282135B2 (ja) * 2014-02-17 2018-02-21 東芝キヤリア株式会社 冷凍サイクル装置
EP3118542B1 (fr) 2014-03-14 2021-05-19 Mitsubishi Electric Corporation Dispositif à cycle de réfrigération
JP2017155944A (ja) 2016-02-29 2017-09-07 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置及びそれを備えた温水暖房装置
JP2017166709A (ja) 2016-03-14 2017-09-21 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置及びそれを備えた温水暖房装置
JP6781034B2 (ja) * 2016-12-14 2020-11-04 三菱重工サーマルシステムズ株式会社 冷媒回路システムおよび冷媒回路システムの制御方法
JP6847239B2 (ja) 2017-09-07 2021-03-24 三菱電機株式会社 空気調和装置

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1026460A1 (fr) * 1998-08-21 2000-08-09 Daikin Industries, Limited Echangeur de chaleur du type a double tube et machine frigorifique utilisant cet echangeur de chaleur
EP1026460A4 (fr) * 1998-08-21 2002-10-23 Daikin Ind Ltd Echangeur de chaleur du type a double tube et machine frigorifique utilisant cet echangeur de chaleur
JP2002243301A (ja) * 2001-02-14 2002-08-28 Daikin Ind Ltd 熱交換ユニット及び空気調和装置
CN100441964C (zh) * 2005-02-03 2008-12-10 乐金电子(天津)电器有限公司 多级型空调器
CN102032725A (zh) * 2010-12-08 2011-04-27 海尔集团公司 过冷装置、具有该装置的空调、控制空调冷媒流量的方法
CN104114964A (zh) * 2012-11-26 2014-10-22 松下电器产业株式会社 制冷循环装置和具备其的热水生成装置
CN104114964B (zh) * 2012-11-26 2016-08-24 松下电器产业株式会社 制冷循环装置和具备其的热水生成装置
WO2022099748A1 (fr) * 2020-11-10 2022-05-19 艾默生环境优化技术(苏州)有限公司 Système de pompe à chaleur

Also Published As

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JPH1068553A (ja) 1998-03-10
AU3783397A (en) 1998-03-19

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