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WO2009087733A1 - Dispositif de cycle de réfrigération et vanne à quatre voies - Google Patents

Dispositif de cycle de réfrigération et vanne à quatre voies Download PDF

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Publication number
WO2009087733A1
WO2009087733A1 PCT/JP2008/003941 JP2008003941W WO2009087733A1 WO 2009087733 A1 WO2009087733 A1 WO 2009087733A1 JP 2008003941 W JP2008003941 W JP 2008003941W WO 2009087733 A1 WO2009087733 A1 WO 2009087733A1
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WO
WIPO (PCT)
Prior art keywords
pipe
heat exchanger
refrigerant
way valve
compressor
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2008/003941
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English (en)
Japanese (ja)
Inventor
Hiroki Murakami
Hiroaki Makino
Tadashi Saito
Yasuhide Hayamaru
Kazuhide Yamamoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2009548813A priority Critical patent/JPWO2009087733A1/ja
Publication of WO2009087733A1 publication Critical patent/WO2009087733A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/0655—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with flat slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/1223—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston one side of the piston being acted upon by the circulating fluid
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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 a refrigeration cycle apparatus and a four-way valve.
  • a compressor In a conventional refrigeration cycle apparatus (air conditioner), a compressor, a first heat exchanger, a first pressure reducing device, a gas-liquid separator, a second pressure reducing device, and a second heat exchanger are sequentially connected by piping.
  • a refrigerant circuit is constituted by the main path and the gas injection path for returning the gas-phase refrigerant separated by the gas-liquid separator to the compressor.
  • the flow direction switched by the first switching unit is locally switched by the second switching unit, so that the refrigerant passing through the decompression path provided with the gas-liquid separator can be used in both the cooling operation and the heating operation.
  • the flow direction is constant.
  • energy efficiency is improved by using the effect of the gas injection path.
  • a four-way valve is used for the first switching means and the second switching means (see, for example, Patent Document 1).
  • a conventional four-way valve has a pair of pistons at both ends, a valve body connected to the piston shaft is provided, a valve chamber in which a high pressure pipe, a low pressure pipe, and a pair of pipes are connected, and a valve A pair of cylinder chambers formed at both ends of the chamber, a pair of conduits connected to the pair of cylinder chambers, a high-pressure conduit connected to the high-pressure piping, and a low-pressure conduit connected to the low-pressure piping, , High pressure and low pressure conduits are connected to the solenoid valve.
  • the solenoid valve the high-pressure pipe is selectively connected to one of the pair of pipes, and the low-pressure pipe is connected to the other pipe.
  • the pressure of each cylinder chamber is switched by switching the solenoid valve,
  • the flow direction is switched by selectively sliding the valve body in the axial direction (see, for example, Patent Document 2).
  • a slow operation element having a constant temperature heating element such as a heater is provided at both ends, and the valve body is pivoted using such a slow operation element.
  • the direction of flow is switched (for example, see Patent Document 3).
  • JP 2001-241797 paragraphs [0019] to [0029], FIG. 1) Japanese Unexamined Patent Publication No. 2002-250457 (paragraph [0016], FIG. 9) Japanese Patent No. 2757997 (FIG. 1)
  • two switching means are arranged in the refrigerant circuit in order to make the flow direction of the refrigerant passing through the decompression path constant in both the cooling operation and the heating operation.
  • a driving device using electric power such as an electromagnetic valve or a constant temperature heating element is required for each four-way valve. It becomes. For this reason, it is necessary to provide two drive units and a control unit and wiring for operating the drive units in the refrigerant circuit, and there is a problem that the air conditioner becomes large and the control becomes complicated.
  • the present invention has been made to solve the above-described problems, and by reducing the number of drive devices for driving the switching means, the refrigeration cycle device can be made compact and simplified. It aims at obtaining the refrigerating cycle device which can be performed. It is another object of the present invention to provide switching means (four-way valve) that does not require a driving device.
  • a refrigeration cycle apparatus is installed in a main path formed by connecting a compressor, a first heat exchanger, a decompression path, and a second heat exchanger by a plurality of pipes, and the main path.
  • the refrigeration cycle apparatus includes a switching unit that connects at least three pipes of the main path, switches a flow path of the valve body to switch an internal flow path, and switches a flow direction of fluid flowing through the main path.
  • the switching means uses at least one main switching means for driving the valve element using electric power, and a pressure change generated in the main path by switching the flow direction of the main path by the main switching means. And at least one subordinate switching means for driving the valve body.
  • the four-way valve forms a switching passage between a pair of pistons that slide in an airtight manner in the main body, a valve chamber provided between the pistons, and a valve seat surface in the valve chamber, A valve body that slides on the valve seat surface in conjunction with the piston, a pair of cylinder chambers provided on both sides of the valve chamber via the piston, a first pipe that is always in communication with the valve chamber, the valve A second pipe that opens to the seat surface and is always in communication with the switching passage, opens to the valve seat surface, and communicates with either the valve chamber or the switching passage in a mutually contradictory relationship due to the switching movement of the valve body.
  • Four-way valve comprising a third pipe and a fourth pipe to be connected, and a pair of conduits connected to the pair of cylinder chambers, one connected to the third pipe and the other to the fourth pipe In the third pipe and the fourth pipe
  • the change in the magnitude of the pressure of the fluid flowing Re respectively is for driving the valve body.
  • the refrigeration cycle apparatus since the number of drive devices for driving the switching means for switching the fluid flow direction is reduced, the refrigeration cycle apparatus can be made compact and the control can be simplified. There is an effect.
  • the flow path can be switched using a pressure change generated according to a change in the fluid flow direction without a driving device, so the four-way valve can be made compact. It is also possible to simplify the control of the four-way valve.
  • Embodiment 1 of this invention It is a section lineblock diagram of a subordinate four-way valve concerning Embodiment 1 of this invention. It is a section lineblock diagram of a subordinate four-way valve concerning Embodiment 1 of this invention. It is a refrigerant circuit figure of the air conditioner by Embodiment 1 of this invention. It is a refrigerant circuit figure of the air conditioner by Embodiment 1 of this invention. It is a refrigerant circuit figure of the air conditioner by Embodiment 1 of this invention. It is a pressure-enthalpy diagram of the air conditioner according to Embodiment 1 of the present invention. It is a refrigerant circuit figure of the air conditioner by Embodiment 2 of this invention.
  • Embodiment 2 It is a pressure-enthalpy diagram of the air conditioner by Embodiment 2 of this invention. It is a refrigerant circuit figure of the air conditioner by Embodiment 3 of this invention. It is a pressure-enthalpy diagram of the air conditioner by Embodiment 3 of this invention. It is a refrigerant circuit figure of the air conditioner by Embodiment 4 of this invention. It is a pressure-enthalpy diagram of the air conditioner by Embodiment 4 of this invention. It is a refrigerant circuit figure of the air conditioner by Embodiment 5 of this invention. It is a pressure-enthalpy diagram of the air conditioner by Embodiment 5 of this invention.
  • Embodiment 6 of this invention It is a refrigerant circuit figure of the air conditioner by Embodiment 6 of this invention. It is a pressure-enthalpy diagram of the air conditioner by Embodiment 6 of this invention. It is a refrigerant circuit figure of the air conditioner by Embodiment 7 of this invention. It is a pressure-enthalpy diagram of the air conditioner by Embodiment 7 of this invention. It is a refrigerant circuit figure of the air conditioner by Embodiment 8 of this invention. It is a pressure-enthalpy diagram of the air conditioner by Embodiment 8 of this invention. It is a refrigerant circuit figure of the air conditioner by Embodiment 9 of this invention.
  • FIG. 10 is a view showing a modification of the dependent four-way valve according to Embodiments 1 to 12 of the present invention.
  • FIG. 10 is a view showing a modification of the dependent four-way valve according to Embodiments 1 to 12 of the present invention.
  • FIG. 10 is a view showing a modification of the dependent four-way valve according to Embodiments 1 to 12 of the present invention. It is a refrigerant circuit diagram of the conventional air conditioner. It is a figure which shows the flow direction of the refrigerant
  • FIG. FIG. 1 is a cross-sectional configuration diagram showing the subordinate switching means 1 mounted on the air conditioner according to the first embodiment.
  • the subordinate switching means 1 of the present embodiment is constituted by a four-way valve, the pressure change that occurs when the flow direction of the main path is changed is not driven by the electric power of the valve body 11 that switches the flow path. The valve body 11 is driven by using it, and the flow path is switched according to the change in the flow direction of the main path.
  • a dependent four-way valve 1 includes a first end cover 19 and a second end cover 20 at both ends of a cylindrical switching means body (four-way valve body) 2 having an inner diameter of about 20 mm.
  • the first pipe 4 having an inner diameter of about 9 mm is provided on the circumferential surface of 2
  • the second pipe 5 having an inner diameter of about 9 mm is provided on the circumferential surface opposite to the first pipe 4, and the second pipe 5
  • a third pipe 6 having an inner diameter of about 9 mm and a fourth pipe 7 having an inner diameter of about 9 mm are installed on both sides.
  • end portions of the second pipe 5, the third pipe 6 and the fourth pipe 7 penetrating into the four-way valve body 2 are connected to the respective pipes and the four-way valve body 2 so as to communicate with each other.
  • a valve seat 21 having one communication hole is provided, and the valve body 11 is provided on the seat of the valve seat 21.
  • the valve body 11 has a concave surface portion facing the valve seat 21, and the valve body 11 slides on the seat surface of the valve seat 21 to move the third pipe 6 or the fourth pipe 7. Either one and the second pipe 5 communicate with each other.
  • the inside of the valve body 11 serves as a folded flow path (switching passage) 11a.
  • the switching valve 12 is formed by connecting the two pistons 9 and the valve body 11 with a plate-like piston shaft 10 having a first communication hole 17 and a second communication hole 18.
  • the piston shaft 10 is rod-shaped, since there is a space between the piston shaft 10 and the four-way valve body 2, the first communication hole 17 and the second communication hole 18 may not be provided.
  • the switching valve 12 slides in the axial direction inside the four-way valve body 2, the valve body 11 slides on the seat surface of the valve seat 21.
  • the four-way valve body 2 includes a valve chamber 3 partitioned by the four-way valve body 2, the first piston 8, the second piston 9, the piston shaft 10, the valve body 11, and the valve seat 21, and the four-way valve body. 2, a first cylinder chamber 13 partitioned by the first end lid 19 and the first piston 8, and a second partition partitioned by the four-way valve body 2, the second end lid 20 and the second piston 9. It can be divided into a cylinder chamber 14, a folded flow path 11 a partitioned by the valve body 11 and the valve seat 21.
  • a first conduit 15 having an inner diameter of about 2 mm is provided so as to communicate the first end lid 19 and the third pipe 6, and the second end lid 20 and the fourth pipe 7 are communicated.
  • a second conduit 16 having an inner diameter of about 2 mm the pressure in the first cylinder chamber 13 is substantially equal to the pressure in the third pipe 6, and the pressure in the second cylinder chamber 14 is the fourth pipe. 7 is almost equal to the pressure.
  • FIG. 1 shows a case where the switching valve 12 moves to the first end lid 19 side
  • FIG. 2 corresponds to a case where the switching valve 12 moves to the second end lid 20 side.
  • the first pipe 4, the second pipe 5, the third pipe 6, and the fourth pipe 7 are connected to the pipes constituting the refrigerant circuit, and the refrigerant passes through the respective pipes.
  • the fourth pipe 7 is connected through the second conduit 16. Fluid flows out to the Further, since the pressure in the valve chamber 3 is substantially equal to that in the first cylinder chamber 13 and is higher than that in the second cylinder chamber 14, the second piston 9 is strongly pressed against the second end cover 20, and the valve chamber 3 does not move to the cylinder chamber 14. Furthermore, since the pressure in the valve chamber 3 communicating with the third pipe 6 is higher than the pressure of the folded flow path 11 a communicating with the fourth pipe 7, the valve body 11 is strongly pressed against the valve seat 21. The fluid in the valve chamber 3 does not move to the return channel 11a.
  • valve chamber 3 Since the pressure in the valve chamber 3 is substantially equal to that in the second cylinder chamber 14 and is higher than that in the first cylinder chamber 13, the first piston 8 is strongly pressed against the first end cover 19, and the valve chamber 3 3 does not move to the cylinder chamber 13. Furthermore, since the pressure of the valve chamber 3 communicating with the fourth pipe 7 is higher than the pressure of the folded flow path 11 a communicating with the third pipe 6, the valve body 11 is strongly pressed against the valve seat 21. The fluid in the valve chamber 3 does not move to the return channel 11a.
  • the subordinate four-way valve 1 guides the pressure of the third pipe 6 to the first cylinder chamber 13 via the first conduit 15 and the pressure of the fourth pipe 7.
  • the dependent four-way valve 1 since the dependent four-way valve 1 has a simple structure that moves the switching valve 12 using only the pressure difference between the third pipe 6 and the fourth pipe 7, it is a four-way valve for switching the refrigerant flow direction. The cost of a single unit can also be reduced.
  • the first pipe chamber 15 is connected to the first cylinder chamber 13 and the third pipe 6 at a distance close to the first cylinder chamber 13, and the second cylinder chamber 14 and the second cylinder chamber 14 are connected to each other. Since the fourth pipe 7 located at a short distance is connected by the second conduit 16, the first conduit 15 and the second conduit 16 can be easily routed. Furthermore, since the length of the first conduit 15 and the second conduit 16 can be shortened, the cost can be reduced.
  • FIGS. 1 and 2 are refrigerant circuit diagrams of an air conditioner equipped with the subordinate four-way valve 1 according to Embodiment 1 of the present invention.
  • FIG. 3 shows the air conditioner performing a cooling operation.
  • 4 corresponds to the case where the air conditioner is performing the heating operation
  • FIG. 5 corresponds to the case where the air conditioner is performing the reheat dehumidifying operation.
  • the compressor 23, the first heat exchanger (outdoor heat exchanger) 25, the decompression path 22, and the second heat exchanger (indoor heat exchanger) 26 are connected by piping. And constitutes the main route. Further, on the main path, main switching means (main four-way valve) 24 for switching between a cooling operation in which the refrigerant discharged from the compressor 23 flows to the outdoor heat exchanger 25 and a heating operation in which the refrigerant flows to the indoor heat exchanger 26. , And a subordinate switching means 1 (subordinate four-way valve) provided at the entrance / exit of the decompression path 22.
  • the decompression path 22 includes a first decompression device 30, a gas-liquid separator 32, and a second decompression device 31, and the main path includes the dependent four-way valve 1, whereby cooling operation and heating are performed.
  • the flow direction of the refrigerant passing through the first pressure reducing device 30, the gas-liquid separator 32, and the second pressure reducing device 31 is made constant.
  • a gas injection pipe 36 for returning the gas-phase refrigerant separated by the gas-liquid separator 32 to the intermediate compression process of the compressor 23 is provided.
  • the main four-way valve 24 is installed downstream of the compressor 23 and performs a switching operation using the electromagnetic valve 43 as in the conventional four-way valve.
  • the subordinate four-way valve 1 is a four-way valve shown in FIGS. 1 and 2, and drives the valve body 11 by utilizing the pressure change generated in the main path when the main four-way valve 24 changes the flow direction of the main path. However, the flow path switching operation is performed.
  • the main four-way valve 24 has four connection ports.
  • the discharge side connection port 44 is connected to a discharge pipe 34 through which high-pressure refrigerant flows out of the compressor 23, and the suction side connection port 45 is connected to a suction pipe 35 that returns to the compressor 23.
  • the first connection port 46 is connected to the outdoor gas pipe 37 connected to the outdoor heat exchanger 25, and the second connection port 47 is connected to the indoor side gas pipe 39 connected to the indoor heat exchanger 26.
  • the main four-way valve 24 may have any structure as long as it can switch the flow direction of the refrigerant, and the drive device for performing the switching operation is not limited to the electromagnetic valve, but has a constant temperature. It may be a heating element or the like, and the driving device may be separate from or integrated with the four-way valve body, and any switching operation may be performed by a driving device using electric power.
  • the main four-way valve 24 is formed with a pair of pistons 8 and 9 to form a valve chamber 3 and a pair of cylinder chambers 13 and 14 in the same manner as the dependent four-way valve 1 shown in FIGS.
  • the discharge pipe 34, the second pipe 5 is connected to the suction pipe 35, the third pipe 6 is connected to the outdoor gas pipe 37, and the fourth pipe 7 is connected to the indoor side gas pipe 39.
  • the conduit 15 and the second conduit 16 are connected to the solenoid valve 43.
  • the main four-way valve 24 can be formed with a simple structure, and costs can be reduced.
  • the inflow pipe 41, the first pressure reducing device (first throttle) 30, the gas-liquid separator 32, the second pressure reducing device (second throttle) are sequentially connected to the first pipe 4. 31 and the outflow pipe 42 are connected, and the second pipe 5 of the subordinate four-way valve 1 is connected to the outflow pipe 42.
  • the third pipe 6 of the subordinate four-way valve 1 is connected to the indoor side liquid pipe 40 connected to the indoor heat exchanger 26, and the fourth pipe 7 is connected to the outdoor side liquid pipe 38 connected to the outdoor heat exchanger 25. Is done.
  • the indoor heat exchanger 26 includes a front heat exchanger 27, a reheat dehumidifying throttle 29, a reheat dehumidifying on-off valve 48, and a rear heat exchanger 28 so that a reheat dehumidifying operation is possible.
  • the injection pipe 36 connecting the injection port provided in the compression process of the compressor 32 and the gas-liquid separator 32 is provided with an injection flow control valve 33 for switching the presence or absence of injection. Yes.
  • FIG. 6 is a pressure-enthalpy diagram, where the solid line indicates the operation of the refrigerant circuit related to the air conditioner shown in the first embodiment, and the alternate long and short dash line (the line connecting ABCDA) is FIG.
  • movement of the refrigerant circuit regarding the conventional air conditioner shown in FIG. A to H and K in FIG. 6 correspond to points A to H and K shown in FIG. 3, FIG. 4, and FIG.
  • a curve W indicates a saturated liquid line and a saturated vapor line of the refrigerant.
  • the inside of the curve W is a gas-liquid two-phase state
  • the left side outside the curve W is a liquid state
  • the right side is a gas state.
  • the compressor 100, the outdoor heat exchanger 102, the pressure reducing device 103, and the indoor heat exchanger 104 are connected by piping to form a main path.
  • the main path is provided with only one main four-way valve 101 that switches between a cooling operation in which the refrigerant discharged from the compressor 100 flows to the outdoor heat exchanger 102 and a heating operation in which the refrigerant flows to the indoor heat exchanger 104.
  • the main four-way valve 101 is driven by a solenoid valve (not shown).
  • a solenoid valve not shown
  • solid arrows indicate the flow direction of the refrigerant during the cooling operation
  • broken line arrows indicate the flow direction of the refrigerant during the heating operation.
  • the refrigerant vapor (point A) compressed to a high pressure by the compressor 100 flows into the outdoor heat exchanger 102 via the main four-way valve 101 and is condensed in the outdoor heat exchanger.
  • point B the pressure is reduced by the pressure reducing device 103 (point C), evaporates in the indoor heat exchanger 104, and returns to the compressor 100 via the main four-way valve 101 (point D) again.
  • the electromagnetic valve 43 is driven, the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47 are connected. Are switched so as to communicate with each other. Further, the reheat dehumidifying on-off valve 48 of the indoor heat exchanger 26 is opened.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the third pipe of the subordinate four-way valve 1 communicating with the suction side of the compressor 23 is increased.
  • the pipe 6 has a low pressure.
  • the switching valve 12 moves to the first end cover 19 side from the operation of the above-described subordinate four-way valve 1 to the state shown in FIG. 1, and the first pipe 4 and the fourth pipe 7 are connected to the valve chamber. 3, the second pipe 5 and the third pipe 6 communicate with each other via the folded flow path 11 a.
  • the high-pressure refrigerant vapor (point E) discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled by the outdoor air in the outdoor heat exchanger 25, which is a condenser, and condensed. Is done.
  • the condensed refrigerant liquid is depressurized by the first pressure reducing device 30 after passing through the subordinate four-way valve 1 (point B), and becomes a gas-liquid two-phase state in which refrigerant vapor and refrigerant liquid of intermediate pressure are mixed. (Point F) flows into the gas-liquid separator 32.
  • the refrigerant vapor (K point) and the refrigerant liquid (G point) are separated, and the separated intermediate pressure refrigerant liquid is further depressurized by the second decompression device 31 (H point), and again.
  • the indoor heat exchanger 26 which is an evaporator.
  • the refrigerant proceeds in sequence to the front-stage heat exchanger 27, the reheat dehumidification on-off valve 48, and the rear-stage heat exchanger 28, and heats from indoor air in the front-stage heat exchanger 27 and the rear-stage heat exchanger 28 that are evaporators. Take away and evaporate.
  • the evaporated refrigerant vapor flows into the compressor 23 after passing through the main four-way valve 24 (D point).
  • the flow rate of the intermediate-pressure refrigerant vapor (point K) separated by the gas-liquid separator 32 is adjusted by the injection flow control valve 33 and passes through the injection pipe 36 in the middle of the compression process of the compressor 23 (The refrigerant at point K) is mixed with the refrigerant at point K and the refrigerant at point I (point J). Further, the refrigerant is compressed to point E and discharged again.
  • the air-liquid separator 32 When the air conditioner shown in Embodiment 1 is air-cooled, the air-liquid separator 32 is provided. Therefore, the enthalpy difference (h3-h1) of the indoor heat exchanger 26 that is an evaporator is the enthalpy of the conventional air conditioner. It becomes larger than the difference (h3 ⁇ h2). Therefore, the evaporation capacity, that is, the cooling capacity is increased as compared with the conventional example. Further, the flow rate of refrigerant flowing through the compressor 23 includes the injection pipe 36, and thus increases due to the flow rate of refrigerant injected from the injection pipe 36 into the compressor 23.
  • the input of the compressor 23 also increases, since the evaporation capacity is larger than that, the coefficient of performance during the cooling operation obtained by dividing the evaporation capacity by the input of the compressor 23 is increased as compared with the conventional example. Further, since the temperature (point E) when discharged from the compressor 23 is lower than that of the conventional example (point A), the reliability of the compressor 23 is improved.
  • the shape of the pressure-enthalpy diagram when the air conditioner is performing the heating operation is substantially the same as that when the cooling operation described with reference to FIG. 6 is performed.
  • the point B and the point C are interchanged.
  • the main four-way valve is driven such that the solenoid valve 43 is driven so that the discharge side connection port 44 and the second connection port 47 communicate with each other and the suction side connection port 45 and the first connection port 46 communicate with each other. 24 is switched. Further, the reheat dehumidifying on-off valve 48 of the indoor heat exchanger 26 is opened.
  • the third pipe 6 of the subordinate four-way valve 1 that communicates with the discharge side of the compressor 23 becomes high pressure
  • the fourth pipe of the subordinate four-way valve 1 that communicates with the suction side of the compressor 23 becomes high pressure
  • the piping 7 becomes a low pressure. Therefore, the switching valve 12 moves to the second end cover 20 side from the operation of the subordinate four-way valve 1 described above to be in the state of FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the refrigerant proceeds in sequence to the rear heat exchanger 28, the reheat dehumidifying on-off valve 48, and the front heat exchanger 27, and is cooled by indoor air in the front heat exchanger 27 and the rear heat exchanger 28 that are condensers. Condensed.
  • the condensed refrigerant liquid is reduced in pressure by the first pressure reducing device 30 after passing through the dependent four-way valve 1 (point B), and becomes a gas-liquid two-phase state in which refrigerant vapor and refrigerant liquid of intermediate pressure are mixed. (Point F) flows into the gas-liquid separator 32.
  • the refrigerant vapor (K point) and the refrigerant liquid (G point) are separated, and the separated intermediate pressure refrigerant liquid is further depressurized by the second decompression device 31 (H point), and again.
  • the process proceeds to the outdoor heat exchanger 25, where the outdoor heat exchanger 25, which is an evaporator, takes heat from the outside air and evaporates.
  • the evaporated refrigerant vapor flows into the compressor 23 after passing through the main four-way valve 24 (point D).
  • the flow rate of the intermediate-pressure refrigerant vapor (point K) separated by the gas-liquid separator 32 is adjusted by the injection flow control valve 33, passes through the injection pipe 36, and passes through the compressor 23.
  • point I the refrigerant at point K and the refrigerant at point I are mixed (point J). Further, the refrigerant is compressed to point E and discharged again.
  • the air conditioner shown in Embodiment 1 When the air conditioner shown in Embodiment 1 is operated for heating, it has a gas-liquid separator 32 and an injection pipe 36, so that the refrigerant flow rate flowing through the indoor heat exchanger 26, which is a condenser, is reduced from the injection pipe 36 to the compressor. It increases with the flow rate of the refrigerant injected into 23. For this reason, the condensing capacity, that is, the heating capacity is increased as compared with the conventional example. Further, the flow rate of the refrigerant flowing through the compressor 23 increases due to the flow rate of the refrigerant injected into the compressor 23 from the injection pipe 36.
  • the input of the compressor 23 also increases, since the condensing capacity is larger than that, the coefficient of performance during the heating operation obtained by dividing the condensing capacity by the input of the compressor 23 is increased as compared with the conventional example. Further, since the temperature (point E) when discharged from the compressor is lower than the conventional example (point A), the reliability of the compressor is improved.
  • the solenoid valve 43 is driven to switch the main four-way valve 24 so that the discharge side connection port 44 and the first connection port 46 communicate with each other and the suction side connection port 45 and the second connection port 47 communicate with each other. Further, the reheat dehumidifying on-off valve 48 is opened and the injection flow control valve 33 is closed, so that at least one of the first decompressor 30 and the second decompressor 31 is not fully opened but throttled.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the third pipe of the subordinate four-way valve 1 communicating with the suction side of the compressor 23 is increased.
  • the pipe 6 has a low pressure.
  • the switching valve 12 moves to the first end cover 19 side from the operation of the dependent four-way valve 1 described above, and the state shown in FIG. 1 is established.
  • the second pipe 5 and the third pipe 6 communicate with each other via the return channel 11a. Thereafter, the reheat dehumidifying on-off valve 48 is closed, and the first decompressor 30 and the second decompressor 31 are fully opened.
  • the high-pressure refrigerant vapor discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled and condensed by the outdoor air in the outdoor heat exchanger 25 that is a condenser.
  • the refrigerant vapor is not completely liquefied by the outdoor heat exchanger 25 and remains in the gas-liquid two-phase state in which the refrigerant vapor and the refrigerant liquid coexist, and the first pressure reducing device via the dependent four-way valve 1. 30, passes through the gas-liquid separator 32 and the second pressure reducing device 31, and again flows into the heat exchanger 26 through the dependent four-way valve 1.
  • the refrigerant that has flowed into the indoor heat exchanger 26 is cooled and condensed by indoor air in a pre-stage heat exchanger 27 that is a condenser, and is then depressurized by a reheat dehumidifying restrictor 29, and is then heated by a post-stage heat that is an evaporator.
  • the exchanger 28 evaporates by taking heat from indoor air.
  • the evaporated refrigerant vapor flows into the compressor 23 via the main four-way valve 24.
  • the indoor air is dehumidified and cooled in the post-stage heat exchanger 28 serving as an evaporator and heated in the pre-stage heat exchanger 27 serving as a condenser, and thus passes through the pre-stage heat exchanger 27 and the post-stage heat exchanger 28.
  • the indoor air can be air-conditioned while dehumidifying.
  • the main four-way valve 24 is set in the same state as in the cooling operation, and the reheat dehumidifying on-off valve 48 is opened, and the injection flow control valve 33 is set. Is closed, and at least one of the first pressure reducing device 30 or the second pressure reducing device 31 is not fully opened but is throttled. Thereafter, in the second stage, the reheat dehumidifying on-off valve 48 is closed, and the first decompressor 30 and the second decompressor 31 are fully opened. The valves and the pressure reducing devices are opened and closed by a control device (not shown).
  • the reheat dehumidifying operation can be performed after the switching valve 12 of the dependent four-way valve 1 is reliably switched to the state shown in FIG. 1, and the first decompressor 30, the gas-liquid separator 32, and
  • the flow direction of the refrigerant passing through the second decompression device 31 can always be a constant direction.
  • coolant which passes through the pressure reduction path 22 while being able to satisfy the pressure reduction amount and flow control amount which the pressure reduction path 22 has, the structural lifetime of the pressure reduction path 22 can be extended.
  • the subordinate four-way valve 1 used in the air conditioner of Embodiment 1 has the configuration shown in FIGS. 1 and 2, so that the subordinate four-way valve 1 is used for cooling operation, heating operation, and reheating.
  • the switching valve of the dependent four-way valve 1 is automatically received in response to the pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1. 12 can be switched.
  • the air conditioner shown in the first embodiment includes the gas-liquid separator 32 in the decompression path 22 and the dependent four-way valve 1 connected to both ends of the decompression path 22, so that the cooling operation or the heating operation is performed.
  • the flow direction of the refrigerant passing through the gas-liquid separator 32 can be made constant by switching the switching valve 12 of the dependent four-way valve 1. Therefore, the refrigerant flows into the gas-liquid separator 32 from the inflow pipe 41 and is separated into the refrigerant liquid and the refrigerant vapor, and the separated refrigerant liquid flows out from the gas-liquid separator 32 through the outflow pipe 42.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a. Strongly pressed. Therefore, the refrigerant does not short-circuit from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the refrigerant may flow in either direction through the gas-liquid separator 32, and before the start of the compressor 23, the reheat dehumidification on-off valve 48 is closed, and the first decompressor 30 and the second decompressor.
  • the device 31 may be left fully open.
  • the pressure difference between the third pipe 6 and the fourth pipe 7 in the reheat dehumidifying operation is smaller than that in the case where the air conditioner performs the cooling operation or the heating operation. Even if the force pressed against the valve seat 21 is reduced and the refrigerant shortcuts from the fourth pipe 7 to the third pipe 6 in the dependent four-way valve 1, there is no problem in the reheat dehumidifying operation.
  • the indoor heat exchanger 26 in order to perform the reheat dehumidification operation, is replaced with the first indoor heat exchanger 27, the rear heat exchanger 28, the reheat dehumidifying throttle 29, the reheat dehumidification.
  • the air conditioner does not perform the reheat dehumidifying operation, only the indoor heat exchanger 28 may be used as the indoor heat exchanger 26.
  • the reheat dehumidification throttle 29 and the reheat dehumidification on-off valve 48 are used in combination. It doesn't matter.
  • injection flow control valve 33 is used to control the flow rate of the refrigerant used for injection, it may be an on-off valve that only switches the presence or absence of injection.
  • the throttle amount of the first decompressor 30 and the throttle amount of the second decompressor 31 are arbitrary, and each of the cooling operation and the heating operation of the air conditioner can be performed by using a decompressor having a variable valve opening. In operation, the optimum operation that maximizes the coefficient of performance is possible.
  • the structure of the compressor 23 is arbitrary, and a refrigerant may be injected between the front stage and the rear stage as a two-stage compressor of the front stage and the rear stage.
  • FIG. FIG. 7 is a refrigerant circuit diagram of an air conditioner according to Embodiment 2 of the present invention.
  • the air conditioner of the second embodiment is different from the first embodiment in that the decompression path 22 does not include the second decompression device 31, but includes the first decompression device 30 and the gas-liquid separator 32. ing. Further, the main path includes the subordinate four-way valve 1 so that the flow direction of the refrigerant passing through the decompression path 22 is constant in both the cooling operation and the heating operation.
  • the injection flow control valve 33 and the injection pipe 36 are not provided. Instead, the gas-liquid returning the gas-phase fluid separated by the gas-liquid separator 32 to the compressor 23.
  • a separation bypass pipe 49 is provided.
  • the gas-liquid separation bypass pipe 49 is connected to the suction pipe 35 of the compressor 23, and is provided with a gas-liquid separation on-off valve 50, a gas-liquid separation check valve 51, and a gas-liquid separation capillary tube 52.
  • the solid line arrows indicate the flow direction of the refrigerant during the cooling operation
  • the broken line arrows indicate the flow direction of the refrigerant during the heating operation.
  • each of the four-way valves 1 and 24 shows a state during cooling operation.
  • the configuration of the indoor heat exchanger 26 includes a front heat exchanger 27, a reheat dehumidifying throttle 29, a reheat dehumidifying on-off valve 48, and a rear heat exchanger. 28, not shown, and an indoor heat exchanger 26.
  • FIG. 8 is a pressure-enthalpy diagram.
  • the solid line indicates the operation of the refrigerant circuit of the air conditioner shown in the second embodiment, and the alternate long and short dash line (the line connecting ABCA-DA) is shown in FIG.
  • movement of the refrigerant circuit of the conventional air conditioner shown in FIG. A to G in the figure correspond to points A to G shown in FIGS.
  • the air conditioner performs a cooling operation.
  • the refrigerant vapor (point A) compressed to a high pressure by the compressor 100 flows into the outdoor heat exchanger 102 via the main four-way valve 101 and is condensed in the outdoor heat exchanger.
  • point B the pressure is reduced by the pressure reducing device 103 (point C), evaporates in the indoor heat exchanger 104, and returns to the compressor 100 via the main four-way valve 101 (point D) again.
  • FIG. 8 is compared with FIG. 6 shown in the first embodiment, the slope of the straight line from the point C to the point D is different in the operation of the conventional example. Strictly speaking, the straight line from the point C to the point D in FIG. 6 has the same inclination as that in FIG. 8 due to pressure loss, but FIG. 6 shows this inclination ignored, and FIG. 8 emphasizes the inclination. Show.
  • the electromagnetic valve 43 is driven, the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47 are communicated.
  • the main four-way valve 24 is switched so as to communicate with each other. Further, the gas-liquid separation on-off valve 50 is opened.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the third pipe of the subordinate four-way valve 1 communicating with the suction side of the compressor 23 is increased.
  • the pipe 6 has a low pressure. For this reason, the switching valve 12 moves to the first end cover 19 side from the operation of the dependent four-way valve 1 described above, and the state shown in FIG. 1 is established.
  • the second pipe 5 and the third pipe 6 communicate with each other via the return channel 11a.
  • the high-pressure refrigerant vapor (point A) discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled by the outdoor air in the outdoor heat exchanger 25, which is a condenser, and condensed. Is done.
  • the condensed refrigerant liquid is depressurized by the first pressure reducing device 30 after passing through the dependent four-way valve 1 (point B), and becomes a gas-liquid two-phase state in which low-pressure refrigerant vapor and refrigerant liquid coexist ( C), and flows into the gas-liquid separator 32.
  • the refrigerant vapor (point F) and the refrigerant liquid (point E) are separated, and the separated refrigerant liquid proceeds to the indoor heat exchanger 26 via the dependent four-way valve 1 and is an evaporator.
  • the indoor heat exchanger 26 evaporates by taking heat from indoor air.
  • the refrigerant vapor that does not contribute to evaporation does not flow into the indoor heat exchanger 26 together with the refrigerant liquid. Therefore, the pressure loss (P1-P2) before and after the refrigerant passes through the indoor heat exchanger 26 is smaller than the pressure loss (P1-P3) of the conventional example.
  • the evaporated refrigerant vapor passes through the main four-way valve 24 (point G) and then proceeds to the compressor 23.
  • the refrigerant vapor (point F) separated by the gas-liquid separator 32 proceeds to the gas-liquid separation capillary tube 52 via the gas-liquid separation on-off valve 50 and the gas-liquid separation check valve 51, and the gas-liquid separation.
  • the refrigerant vapor that has passed through the main four-way valve 24 is merged (point G) and flows into the compressor 23.
  • the refrigerant vapor that has flowed into the compressor 23 is compressed to point A and discharged again.
  • the air-liquid separator 32 When the air conditioner shown in Embodiment 2 is air-cooled, the air-liquid separator 32 is provided, so that the enthalpy difference (h3-h1) of the indoor heat exchanger 26 that is an evaporator is the enthalpy of the conventional air conditioner. It becomes larger than the difference (h3-h2). Therefore, the evaporation capacity, that is, the cooling capacity is increased as compared with the conventional example. Further, since only the refrigerant liquid from the gas-liquid separator 32 flows into the indoor heat exchanger 26, the pressure loss of the indoor heat exchanger 26 that is an evaporator is reduced, and the suction pressure of the compressor 23 is increased. Therefore, when the air conditioner is operated so that the evaporation capacity is constant, the input of the compressor 23 decreases, and the coefficient of performance during cooling operation obtained by dividing the evaporation capacity by the input of the compressor 23 is conventionally More than the example.
  • the shape of the pressure-enthalpy diagram when the heating operation is performed is almost equal to that in FIG.
  • the point B and the point C are interchanged.
  • the solenoid valve 43 is driven to switch the main four-way valve 24 so that the discharge side connection port 44 and the second connection port 47 communicate with each other and the suction side connection port 45 and the first connection port 46 communicate with each other. Further, the gas-liquid separation on-off valve 50 is opened.
  • the compressor 23 is driven, the third pipe 6 of the subordinate four-way valve 1 that communicates with the discharge side of the compressor 23 becomes high pressure, while the fourth pipe of the subordinate four-way valve 1 that communicates with the suction side of the compressor 23.
  • the piping 7 becomes a low pressure. Therefore, the switching valve 12 moves to the second end cover 20 side from the operation of the subordinate four-way valve 1 described above to be in the state of FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor (point A) discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24, and is cooled by indoor air in the indoor heat exchanger 26 that is a condenser. , Condensed.
  • the condensed refrigerant liquid is depressurized by the first pressure reducing device 30 after passing through the dependent four-way valve 1 (point B), and becomes a gas-liquid two-phase state in which low-pressure refrigerant vapor and refrigerant liquid coexist ( C), and flows into the gas-liquid separator 32.
  • the refrigerant vapor (point F) and the refrigerant liquid (point E) are separated, and the separated refrigerant liquid passes through the dependent four-way valve 1 and then proceeds to the outdoor heat exchanger 25, where In the outdoor heat exchanger 25, the heat is taken from the outside air to evaporate.
  • the evaporated refrigerant vapor passes through the main four-way valve 24 (point G) and then proceeds to the compressor 23.
  • the refrigerant vapor (point F) separated by the gas-liquid separator 32 proceeds to the gas-liquid separation capillary tube 52 via the gas-liquid separation on-off valve 50 and the gas-liquid separation check valve 51, and the gas-liquid separation.
  • the refrigerant vapor that has passed through the main four-way valve 24 is merged (point G) and flows into the compressor 23.
  • the refrigerant vapor that has flowed into the compressor 23 is compressed to point A and discharged again.
  • the subordinate four-way valve 1 used in the air conditioner of the second embodiment has the configuration shown in FIGS. 1 and 2, the subordinate four-way valve 1 is used for cooling as in the first embodiment.
  • the switching of the dependent four-way valve 1 is automatically performed in response to the pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1.
  • the valve 12 can be switched.
  • the air conditioner shown in the second embodiment includes the gas-liquid separator 32 in the decompression path 22 and the dependent four-way valve 1 connected to both ends of the decompression path 22, so that the cooling operation or the heating operation is performed.
  • the flow direction of the gas-liquid separator 32 can be made constant by switching the switching valve 12 of the dependent four-way valve 1. Therefore, the refrigerant flows into the gas-liquid separator 32 from the inflow pipe 41 and is separated into the refrigerant liquid and the refrigerant vapor, and the separated refrigerant liquid passes from the gas-liquid separator 32 through the outflow pipe 42 to the outdoor heat exchanger.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21. Therefore, the refrigerant does not short-circuit from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the reheat dehumidifying operation can be performed by making the configuration of the indoor heat exchanger 26 the same as in the first embodiment.
  • a gas-liquid separation flow control valve is provided to pass through the gas-liquid separation bypass pipe 49. The flow rate of the refrigerant vapor may be adjusted.
  • FIG. 9 is a refrigerant circuit diagram of an air conditioner according to Embodiment 3 of the present invention.
  • the decompression path 22 does not include the second decompression device 31 and the gas-liquid separator 32, and the first decompression device 30 and the first decompression device 1 supercooling heat exchanger 53 (provided on the upstream side of the first decompression device 30).
  • the main path includes the subordinate four-way valve 1 so that the flow direction of the refrigerant passing through the decompression path 22 is constant in both the cooling operation and the heating operation.
  • the injection flow control valve 33 and the injection pipe 36 are not provided, but a supercooling injection pipe 55 is provided instead.
  • the supercooling injection pipe 55 is branched from between the sub four-way valve 1 and the first supercooling heat exchanger 53 (point B), and the supercooling pressure reducing device 54 that makes the branched refrigerant an intermediate pressure, and 1 is connected to an injection port provided in the middle of the compression process of the compressor 32 via a supercooling heat exchanger 53.
  • the intermediate-pressure refrigerant after passing through the supercooling decompression device 54 and the high-pressure refrigerant passing through the subordinate four-way valve 1 exchange heat.
  • the solid line arrows indicate the flow direction of the refrigerant during the cooling operation
  • the broken line arrows indicate the flow direction of the refrigerant during the heating operation.
  • each of the four-way valves 1 and 24 shows a state during cooling operation.
  • FIG. 10 is a pressure-enthalpy diagram, where the solid line indicates the operation of the refrigerant circuit of the air conditioner shown in the third embodiment, and the alternate long and short dash line (the line connecting ABCDA) is shown in FIG.
  • movement of the refrigerant circuit of the conventional air conditioner shown in FIG. A to H and K in the figure correspond to points A to H and K shown in FIG. 9 and FIG.
  • the air conditioner performs a cooling operation.
  • the operation of the conventional air conditioner is the same as that of the conventional operation shown in FIG. 6, and in FIG. 10, the inclination of the straight line from the C point to the D point is ignored.
  • the electromagnetic valve 43 is driven so that the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47 are connected.
  • the main four-way valve 24 is switched so as to communicate with each other.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the third pipe of the subordinate four-way valve 1 communicating with the suction side of the compressor 23 is increased.
  • the pipe 6 has a low pressure.
  • the switching valve 12 moves to the first end cover 19 side from the operation of the dependent four-way valve 1 described above, and the state shown in FIG. 1 is established.
  • the second pipe 5 and the third pipe 6 communicate with each other via the return channel 11a.
  • the high-pressure refrigerant vapor (point E) discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 through the main four-way valve 24, and is cooled by the outdoor air in the outdoor heat exchanger 25, which is a condenser, and condensed. Is done.
  • the condensed refrigerant liquid passes through the dependent four-way valve 1 (point B), and is further cooled by an intermediate-pressure refrigerant that flows oppositely in the first subcooling heat exchanger 53 (point F).
  • point H After being depressurized by the decompression device 30 (point H), the process proceeds to the indoor heat exchanger 26 via the dependent four-way valve 1 and evaporates by taking heat from the indoor air in the indoor heat exchanger 26 that is an evaporator.
  • the evaporated refrigerant vapor passes through the main four-way valve 24 (D point) and then proceeds to the compressor 23.
  • a part of the refrigerant liquid branched to the supercooling injection pipe 55 at point B is decompressed to an intermediate pressure by the supercooling decompression device 54 (point G), and then the first supercooling heat exchanger 53.
  • the first supercooling heat exchanger 53 When the air conditioner shown in Embodiment 3 is air-cooled, the first supercooling heat exchanger 53 is provided, so that the enthalpy difference (h3-h1) of the indoor heat exchanger 26, which is an evaporator, It becomes larger than the enthalpy difference (h3 ⁇ h2) of the harmonic machine. Therefore, the evaporation capacity, that is, the cooling capacity is increased as compared with the conventional example. Further, since the supercooling injection pipe 55 is provided, the flow rate of the refrigerant flowing through the compressor 23 is increased by the flow rate of the refrigerant injected from the supercooling injection pipe 55 into the compressor 23.
  • the input of the compressor 23 also increases, since the evaporation capacity is larger than that, the coefficient of performance during the cooling operation obtained by dividing the evaporation capacity by the input of the compressor 23 is increased as compared with the conventional example. Further, since the temperature when discharged from the compressor is lower than that of the conventional example, the reliability of the compressor is improved.
  • the shape of the pressure-enthalpy diagram when the heating operation is performed is almost equal to that in FIG. However, when heating the conventional air conditioner shown in FIG. 29, the points B and C are interchanged.
  • the solenoid valve 43 is driven to switch the main four-way valve 24 so that the discharge side connection port 44 and the second connection port 47 communicate with each other and the suction side connection port 45 and the first connection port 46 communicate with each other.
  • the compressor 23 is driven, the third pipe 6 of the subordinate four-way valve 1 that communicates with the discharge side of the compressor 23 becomes high pressure, while the fourth pipe of the subordinate four-way valve 1 that communicates with the suction side of the compressor 23.
  • the piping 7 becomes a low pressure.
  • the switching valve 12 moves to the second end cover 20 side from the operation of the subordinate four-way valve 1 described above to be in the state of FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor (point E) discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24, and is cooled by indoor air in the indoor heat exchanger 26 that is a condenser. , Condensed.
  • the condensed refrigerant liquid passes through the dependent four-way valve 1 (point B), it is further cooled by the intermediate pressure refrigerant flowing oppositely in the first subcooling heat exchanger 53 (point F), and the first After the pressure is reduced by the pressure reducing device 30 (point H), the process proceeds to the outdoor heat exchanger 25 via the dependent four-way valve 1, and the outdoor heat exchanger 25, which is an evaporator, takes heat from the outside air and evaporates.
  • the evaporated refrigerant vapor passes through the main four-way valve 24 (D point) and then proceeds to the compressor 23.
  • a part of the refrigerant liquid branched to the supercooling injection pipe 55 at point B is decompressed to an intermediate pressure by the supercooling decompression device 54 (point G), and then the first supercooling heat exchanger 53.
  • the supercooling injection pipe 55 When the air conditioner shown in Embodiment 3 is heated, the supercooling injection pipe 55 is provided. Therefore, the refrigerant flow rate flowing through the indoor heat exchanger 26 as a condenser is changed from the supercooling injection pipe 55 to the compressor 23. It increases with the flow rate of the refrigerant injected into the tank. For this reason, the condensing capacity, that is, the heating capacity is increased as compared with the conventional example. Further, the flow rate of refrigerant flowing through the compressor 23 increases due to the flow rate of refrigerant injected into the compressor 23 from the supercooling injection pipe 55.
  • the input of the compressor 23 also increases, since the condensing capacity is larger than that, the coefficient of performance during the heating operation obtained by dividing the condensing capacity by the input of the compressor 23 is increased as compared with the conventional example. Moreover, since the temperature when discharged from the compressor 23 is lower than that of the conventional example, the reliability of the compressor 23 is improved.
  • the subordinate four-way valve 1 used in the air conditioner of the third embodiment has the configuration shown in FIGS. 1 and 2, and thus the subordinate four-way valve 1 was used for cooling operation and heating operation.
  • the switching valve 12 of the dependent four-way valve 1 can be automatically switched in response to a pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1. it can.
  • the decompression path 22 includes the first decompression device 30 and the first supercooling heat exchanger 53, and the subordinate four-way valve is disposed at both ends of the decompression path 22. 1 and a path for flowing the high-pressure refrigerant to the first decompression device 30 before the high-pressure refrigerant flows into the first decompression device 30 in both the cooling operation and the heating operation, and a supercooling decompression device
  • the pressure is reduced to an intermediate pressure by 54 and branched to an injection path for returning to the intermediate compression process of the compressor 23.
  • the first supercooling heat exchanger 53 is provided so that the refrigerant after passing through the supercooling decompression device 54 and the refrigerant flowing into the first decompression device 30 exchange heat. Therefore, the capacity and the coefficient of performance can be increased in both the cooling operation and the heating operation of the air conditioner. Further, the reliability of the compressor is improved.
  • the high-pressure refrigerant and the intermediate-pressure refrigerant branched in front of the first subcooling heat exchanger 53 flow oppositely in the first subcooling heat exchanger 53. Since it did in this way, the heat exchange performance of the 1st subcooling heat exchanger 53 can be improved.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21.
  • the fourth pipe 7 there is no shortcut from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the structure of the 1st subcooling heat exchanger 53 is arbitrary, and the refrigerant
  • the flow of the high-pressure refrigerant and the intermediate-pressure refrigerant that passes through the first subcooling heat exchanger 53 is opposed, but it may be parallel flow.
  • the description of the reheat dehumidification operation is omitted, but the reheat dehumidification operation can be performed by making the configuration of the indoor heat exchanger 26 the same as in the first embodiment.
  • FIG. 11 is a refrigerant circuit diagram of an air conditioner according to Embodiment 4 of the present invention.
  • the air conditioner of the fourth embodiment includes a supercooling bypass pipe 70 instead of the supercooling injection pipe 55.
  • the subcooling bypass pipe 70 is branched from the point where the sub four-way valve 1 and the first subcooling heat exchanger 53 are reached (point B), and the subcooling decompression device 54 and the first subcooling heat exchanger are branched. 53, a supercooling on-off valve 56, a supercooling check valve 57, and a supercooling capillary tube 58 are connected to a suction pipe 35 connected to the compressor 23.
  • each of the four-way valves 1 and 24 shows a state during cooling operation.
  • FIG. 12 is a pressure-enthalpy diagram, where the solid line indicates the operation of the refrigerant circuit of the air conditioner shown in the fourth embodiment, and the alternate long and short dash line (the line connecting ABCDA) is shown in FIG.
  • movement of the refrigerant circuit of the conventional air conditioner shown in FIG. A to I in the figure correspond to points A to I shown in FIG. 11 and FIG.
  • the air conditioner performs a cooling operation.
  • the operation of the conventional air conditioner is the same as the conventional operation shown in FIG. 8, and in FIG. 12, the inclination of the straight line from the point C to the point D is emphasized as compared with the case of FIG.
  • the electromagnetic valve 43 is driven, the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47.
  • the main four-way valve 24 is switched so as to communicate with each other. Further, the supercooling on-off valve 56 is opened.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the third pipe of the subordinate four-way valve 1 communicating with the suction side of the compressor 23 is increased.
  • the pipe 6 has a low pressure.
  • the switching valve 12 moves to the first end cover 19 side from the operation of the dependent four-way valve 1 described above, and the state shown in FIG. 1 is established.
  • the second pipe 5 and the third pipe 6 communicate with each other via the return channel 11a.
  • the high-pressure refrigerant vapor (point A) discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled by the outdoor air in the outdoor heat exchanger 25, which is a condenser, and condensed. Is done.
  • the condensed refrigerant liquid passes through the dependent four-way valve 1 (point B), and is further cooled by an intermediate-pressure refrigerant flowing oppositely in the first subcooling heat exchanger 53 (point E).
  • point F After being depressurized by the decompression device 30 (point F), the process proceeds to the indoor heat exchanger 26 via the subordinate four-way valve 1, and evaporates by taking heat from the indoor air in the indoor heat exchanger 26 that is an evaporator.
  • the proportion of the refrigerant vapor that does not contribute to evaporation is smaller at the point F than the proportion of the refrigerant vapor at the point C. Therefore, the indoor heat exchanger together with the refrigerant liquid
  • the refrigerant vapor flowing into the refrigerant 26 is small, and the pressure loss (P1-P2) before and after the refrigerant passes through the indoor heat exchanger 26 is smaller than the pressure loss (P1-P3) of the conventional example.
  • the refrigerant vapor evaporated in the indoor heat exchanger 26 passes through the main four-way valve 24 (point G) and then proceeds to the compressor 23.
  • a part of the refrigerant liquid branched into the supercooling bypass pipe 70 at the point B is decompressed to an intermediate pressure by the supercooling decompression device 54 (point H), and then the first supercooling heat exchanger 53.
  • the heat is removed from the high-pressure refrigerant flowing in the opposite direction and evaporated (point I), and then proceeds to the supercooling capillary tube 58 via the supercooling on-off valve 56 and the supercooling check valve 57, and the supercooling capillary tube After being depressurized at 58, it merges with the refrigerant vapor that has passed through the main four-way valve 24 (point G) and flows into the compressor 23.
  • the refrigerant vapor that has flowed into the compressor 23 is compressed to point A and discharged again.
  • the first supercooling heat exchanger 53 is provided, so that the enthalpy difference (h3-h1) of the indoor heat exchanger 26, which is an evaporator, It becomes larger than the enthalpy difference (h3 ⁇ h2) of the harmonic machine. Therefore, the evaporation capacity, that is, the cooling capacity is increased as compared with the conventional example. Moreover, the pressure loss of the indoor heat exchanger 26 as an evaporator is reduced, and the suction pressure of the compressor 23 is increased. Therefore, when the air conditioner is operated so that the evaporation capacity is constant, the input of the compressor 23 decreases, and the coefficient of performance during cooling operation obtained by dividing the evaporation capacity by the input of the compressor 23 is conventionally More than the example.
  • the shape of the pressure-enthalpy diagram when the heating operation is performed is almost the same as FIG.
  • the point B and the point C are interchanged.
  • the solenoid valve 43 is driven to switch the main four-way valve 24 so that the discharge side connection port 44 and the second connection port 47 communicate with each other and the suction side connection port 45 and the first connection port 46 communicate with each other.
  • the gas-liquid separating on-off valve 56 is opened.
  • the piping 7 becomes a low pressure. Therefore, the switching valve 12 moves to the second end cover 20 side from the operation of the subordinate four-way valve 1 described above to be in the state of FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor (point A) discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24, and is cooled by indoor air in the indoor heat exchanger 26 that is a condenser. , Condensed.
  • the condensed refrigerant liquid passes through the dependent four-way valve 1 (point B), and is further cooled by an intermediate-pressure refrigerant flowing oppositely in the first subcooling heat exchanger 53 (point E).
  • point F After being depressurized by the decompression device 30 (point F), the process proceeds to the outdoor heat exchanger 25 via the dependent four-way valve 1 and evaporates by taking heat from the outside air in the outdoor heat exchanger 25 that is an evaporator.
  • the evaporated refrigerant vapor passes through the main four-way valve 24 (point G) and then proceeds to the compressor 23.
  • a part of the refrigerant liquid branched into the supercooling bypass pipe 70 at the point B is decompressed to an intermediate pressure by the supercooling decompression device 54 (point H), and then the first supercooling heat exchanger 53.
  • the heat is removed from the high-pressure refrigerant flowing in the opposite direction and evaporated (point I), and then proceeds to the supercooling capillary tube 58 via the supercooling on-off valve 56 and the supercooling check valve 57, and the supercooling capillary tube After being depressurized at 58, it merges with the refrigerant vapor that has passed through the main four-way valve 24 (point G) and flows into the compressor 23.
  • the refrigerant vapor that has flowed into the compressor 23 is compressed to point A and discharged again.
  • the pressure loss (P1-P2) of the outdoor heat exchanger 25 serving as an evaporator is reduced, so that the intake temperature of the compressor rises and the air conditioner Refrigerant circulation flow rate increases. For this reason, the condensing capacity, that is, the heating capacity is increased as compared with the conventional example. Further, when the air conditioner is operated so that the condensing capacity becomes constant due to the increase of the suction pressure of the compressor (P2-P3), the input of the compressor is reduced and the condensing capacity is reduced to the input of the compressor 23. The coefficient of performance at the time of heating operation obtained by dividing by is increased from the conventional example.
  • the subordinate four-way valve 1 used in the air conditioner of the fourth embodiment has the configuration shown in FIGS. 1 and 2, and thus the subordinate four-way valve 1 was used for cooling operation and heating operation.
  • the switching valve 12 of the dependent four-way valve 1 can be automatically switched in response to a pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1. it can.
  • the decompression path 22 includes the first decompression device 30 and the first subcooling heat exchanger 53, and the subordinate four-way valve is disposed at both ends of the decompression path 22. 1 and a path for flowing the high-pressure refrigerant to the first decompression device 30 before the high-pressure refrigerant flows into the first decompression device 30 in both the cooling operation and the heating operation, and a supercooling decompression device
  • the pressure is reduced to an intermediate pressure by 54 and branched to a subcooling bypass path that returns to the compressor 23.
  • the first supercooling heat exchanger 53 is provided so that the refrigerant after passing through the supercooling decompression device 54 and the refrigerant flowing into the first decompression device 30 exchange heat. Therefore, the capacity and the coefficient of performance can be increased in both the cooling operation and the heating operation of the air conditioner.
  • the high-pressure refrigerant and the intermediate-pressure refrigerant branched in front of the first supercooling heat exchanger 53 by the switching of the switching valve 12 of the subordinate four-way valve 1 are the first refrigerant. Therefore, the heat exchange performance of the first supercooling heat exchanger 53 can be improved.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21.
  • the fourth pipe 7 there is no shortcut from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the structure of the 1st subcooling heat exchanger 53 is arbitrary, and the refrigerant
  • the flow of the high-pressure refrigerant and the intermediate-pressure refrigerant that passes through the first subcooling heat exchanger 53 is opposed, but it may be parallel flow.
  • the description of the reheat dehumidification operation is omitted, but the reheat dehumidification operation can be performed by making the configuration of the indoor heat exchanger 26 the same as in the first embodiment.
  • a supercooling flow rate control valve is provided so that the flow rate of the refrigerant vapor passing through the supercooling bypass pipe 70 is increased. You may adjust.
  • FIG. 13 is a refrigerant circuit diagram of an air conditioner according to Embodiment 5 of the present invention.
  • the decompression path 22 does not include the second decompression device 31, and the first decompression device 30 and the gas-liquid separator 32 (first And an ejector 61 (provided on the upstream side of the gas-liquid separator 32).
  • the main path includes the subordinate four-way valve 1 so that the flow direction of the refrigerant passing through the decompression path 22 is constant in both the cooling operation and the heating operation.
  • the ejector 61 includes a nozzle 59 and a diffuser 60, and the nozzle 59 and the diffuser 60 are connected to the suction pipe 35 by an ejector pipe 62. Further, the ejector piping 62 includes an ejector decompression device 63. Further, similarly to the first embodiment, a gas injection pipe 36 for returning the gas-phase refrigerant separated by the gas-liquid separator 32 to the intermediate compression process of the compressor 23 is provided. Moreover, in the figure, the solid line arrows indicate the flow direction of the refrigerant during the cooling operation, and the broken line arrows indicate the flow direction of the refrigerant during the heating operation. In the figure, each of the four-way valves 1 and 24 shows a state during cooling operation.
  • FIG. 14 is a pressure-enthalpy diagram, where the solid line indicates the operation of the refrigerant circuit of the air conditioner shown in the fifth embodiment, and the alternate long and short dash line (the line connecting ABCDA) is shown in FIG.
  • movement of the refrigerant circuit of the conventional air conditioner shown in FIG. A to L in the figure correspond to points A to L shown in FIG. 13 and FIG.
  • the air conditioner performs a cooling operation.
  • the operation of the conventional air conditioner is the same as that of the conventional operation shown in FIG. 6, and in FIG. 14, the inclination of the straight line from the C point to the D point is ignored.
  • the solenoid valve 43 is driven, the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47.
  • the main four-way valve 24 is switched so as to communicate with each other.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the third pipe of the subordinate four-way valve 1 communicating with the suction side of the compressor 23 is increased.
  • the pipe 6 has a low pressure.
  • the switching valve 12 moves to the first end cover 19 side from the operation of the above-described subordinate four-way valve 1 to the state shown in FIG. 1, and the first pipe 4 and the fourth pipe 7 are connected to the valve chamber. 3, the second pipe 5 and the third pipe 6 communicate with each other via the folded flow path 11 a.
  • the high-pressure refrigerant vapor (point E) discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled by the outdoor air in the outdoor heat exchanger 25, which is a condenser, and condensed. Is done.
  • the condensed refrigerant liquid passes through the dependent four-way valve 1 (point B), and then expands and accelerates while changing the isentropy at the nozzle 59 of the ejector 61 (point F), and is ejector piping at the inlet of the diffuser 60.
  • the refrigerant vapor (point D) that has passed through 62 is attracted and mixed (point G), and the pressure is recovered by the diffuser 60 (point H).
  • the pressure-recovered refrigerant flows into the gas-liquid separator 32 in a gas-liquid two-phase state, and is separated into refrigerant vapor (point L) and refrigerant liquid (point I).
  • the separated refrigerant liquid is the first decompression device.
  • point J After the pressure is further reduced at 30 (point J), it flows into the indoor heat exchanger 26 via the dependent four-way valve 1.
  • the refrigerant evaporates by taking heat from indoor air in the indoor heat exchanger 26 that is an evaporator, and flows into the compressor 23 through the main four-way valve 24 (point K).
  • the flow rate of the intermediate-pressure refrigerant vapor (point L) separated by the gas-liquid separator 32 is adjusted by the injection flow control valve 33, passes through the injection pipe 36, and is in the middle of the compression process of the compressor 23 (
  • the refrigerant at point L and the refrigerant at point M are mixed (point N). Further, the refrigerant is compressed to point E and discharged again.
  • the refrigerant vapor after evaporating in the indoor heat exchanger 26 and passing through the main four-way valve 24 (point K) is branched from the middle of the suction pipe 35 to the ejector pipe 62 and decompressed by the ejector decompression device 63. Later (D point), it is attracted and mixed by the high-speed refrigerant (F point) that has passed through the nozzle 59 (G point).
  • the air conditioner shown in Embodiment 5 When the air conditioner shown in Embodiment 5 is air-cooled, it includes the ejector 61 and the gas-liquid separator 32. Therefore, the enthalpy difference (h3-h1) of the indoor heat exchanger 26, which is an evaporator, is reduced by the conventional air conditioner. It becomes larger than the enthalpy difference (h3-h2) of the machine. Therefore, the evaporation capacity, that is, the cooling capacity is increased as compared with the conventional example. Further, when the air conditioner is operated so that the evaporation capacity is constant, the input of the compressor 23 is reduced by the pressure increase (P1-P2) due to the use of the ejector 61, and the evaporation capacity is reduced to the compressor 23.
  • P1-P2 the pressure increase
  • the coefficient of performance at the time of cooling operation obtained by dividing by the input is increased as compared with the conventional example. Further, since the ejector pipe 62 is provided, a part of the refrigerant vapor evaporated by the indoor heat exchanger 26 is sucked by the ejector 61, boosted by the diffuser 60, separated by the gas-liquid separator 32, and injected by the injection pipe 36. To the compressor 23. Thereby, the input to the compressor 23 decreases. Further, since the temperature (point E) when discharged from the compressor 23 is lower than that of the conventional example (point A), the reliability of the compressor 23 is improved.
  • the shape of the pressure-enthalpy diagram when the heating operation is performed is almost the same as that in FIG.
  • the point B and the point C are interchanged.
  • the solenoid valve 43 is driven to switch the main four-way valve 24 so that the discharge side connection port 44 and the second connection port 47 communicate with each other and the suction side connection port 45 and the first connection port 46 communicate with each other.
  • the compressor 23 is driven, the third pipe 6 of the subordinate four-way valve 1 that communicates with the discharge side of the compressor 23 becomes high pressure, while the fourth pipe of the subordinate four-way valve 1 that communicates with the suction side of the compressor 23.
  • the piping 7 becomes a low pressure.
  • the switching valve 12 moves to the second end cover 20 side from the operation of the subordinate four-way valve 1 described above to be in the state of FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor (point E) discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24 and is cooled by indoor air in the indoor heat exchanger 26 that is a condenser. , Condensed.
  • the condensed refrigerant liquid passes through the subordinate four-way valve 1 (point B), then expands and accelerates while changing the isentropy at the nozzle 59 (point F), and passes through the ejector pipe 62 at the inlet of the diffuser 60.
  • the refrigerant vapor (D point) is attracted and mixed (G point), and the pressure is restored by the diffuser 60 (H point).
  • the pressure-recovered refrigerant flows into the gas-liquid separator 32 in a gas-liquid two-phase state, and is separated into refrigerant vapor (point L) and refrigerant liquid (point I).
  • the separated refrigerant liquid is the first decompression device.
  • the refrigerant flows into the outdoor heat exchanger 25 via the dependent four-way valve 1.
  • the refrigerant evaporates by taking heat from the outside air in the outdoor heat exchanger 25 that is an evaporator, and flows into the compressor 23 through the main four-way valve 24 (point K).
  • the flow rate of the intermediate-pressure refrigerant vapor (point L) separated by the gas-liquid separator 32 is adjusted by the injection flow control valve 33, passes through the injection pipe 36, and is in the middle of the compression process of the compressor 23 (
  • the refrigerant at point L and the refrigerant at point M are mixed (point N). Further, the refrigerant is compressed to point E and discharged again.
  • the refrigerant vapor after passing through the main four-way valve 24 (point K) is branched from the middle of the suction pipe 35 to the ejector pipe 62 and decompressed by the ejector decompression device 63 (point D). It is attracted and mixed by the high-speed refrigerant (F point) that has passed (G point).
  • the refrigerant flow rate flowing through the indoor heat exchanger 26 that is a condenser is the refrigerant flow rate injected into the compressor 23 from the injection pipe 36. Increase by. For this reason, the condensing capacity, that is, the heating capacity is increased as compared with the conventional example. Moreover, since the temperature when discharged from the compressor 23 is lower than that of the conventional example, the reliability of the compressor 23 is improved.
  • the ejector 61 is provided, so that the input of the compressor 23 is reduced by the pressure increase (P1-P2) due to the use of the ejector 61,
  • the coefficient of performance at the time of heating operation obtained by dividing the condensation capacity by the input of the compressor 23 is increased as compared with the conventional example.
  • the ejector pipe 62 is provided, a part of the refrigerant vapor evaporated by the outdoor heat exchanger 25 is sucked by the ejector 61, boosted by the diffuser 60, separated by the gas-liquid separator 32, and injected by the injection pipe 36. To the compressor 23. Thereby, the input to the compressor 23 decreases.
  • the subordinate four-way valve 1 used in the air conditioner of the fifth embodiment has the configuration shown in FIGS. 1 and 2, and thus the subordinate four-way valve 1 was used for cooling operation and heating operation.
  • the switching valve 12 of the dependent four-way valve 1 can be automatically switched in response to a pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1. it can.
  • the decompression path 22 includes the first decompression device 30, the gas-liquid separator 32, and the ejector 61, and the subordinate four-way valve 1 is disposed at both ends of the decompression path 22.
  • the high-pressure refrigerant flows into the ejector 61, expands by isentropic change at the nozzle 59, and sucks the refrigerant vapor through the ejector pipe 62.
  • the pressure is recovered by the diffuser 60, it flows into the gas-liquid separator 32 in a gas-liquid two-phase state, and is further separated into the refrigerant vapor and the refrigerant liquid by the gas-liquid separator 32.
  • the ejector 61 and the gas-liquid separator 32 function such that the refrigerant is depressurized by the first pressure reducing device 30 and then the separated refrigerant vapor flows out through the gas-liquid separation pipe 49. It is possible to form a flow of the refrigerant that works. Therefore, in both the cooling operation and the heating operation of the air conditioner, the capacity and the coefficient of performance can be increased, and the reliability of the compressor is improved.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21.
  • the fourth pipe 7 there is no shortcut from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the description of the reheat dehumidification operation is omitted, but the reheat dehumidification operation can be performed by making the configuration of the indoor heat exchanger 26 the same as in the first embodiment.
  • FIG. 15 is a refrigerant circuit diagram of an air conditioner according to Embodiment 6 of the present invention.
  • the air conditioner of the sixth embodiment is different from the fifth embodiment in that the suction side connection port 45 of the main four-way valve 24 is not connected to the suction pipe 35 but is connected to the ejector pipe 62.
  • the injection pipe 36 and the injection flow control valve 33 are not provided. Instead, the gas-liquid separator 32 and the suction pipe 35 are connected by a gas-liquid separation return pipe 71 for gas-liquid separation.
  • the return pipe 71 includes a gas-liquid separation return flow valve 64.
  • each of the four-way valves 1 and 24 shows a state during cooling operation.
  • FIG. 16 is a pressure-enthalpy diagram, where the solid line indicates the operation of the refrigerant circuit of the air conditioner shown in the sixth embodiment, and the alternate long and short dash line (the line connecting ABCDA) is FIG.
  • movement of the refrigerant circuit of the conventional air conditioner shown in FIG. A to K in the figure correspond to points A to K shown in FIG. 15 and FIG.
  • the air conditioner performs a cooling operation.
  • the operation of the conventional air conditioner is the same as that of the conventional operation shown in FIG. 6, and also in FIG. 16, the inclination of the straight line from the point C to the point D is ignored.
  • the solenoid valve 43 is driven, the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47 are connected.
  • the main four-way valve 24 is switched so as to communicate with each other.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the gas-liquid separation return pipe 71 and the gas pipe are connected to the suction side of the compressor 23.
  • the third pipe 6 of the subordinate four-way valve 1 communicating with the liquid separator 32, the diffuser 60, the ejector pipe 62, the main four-way valve 24, the indoor side gas pipe 39, the indoor heat exchanger 26, and the indoor side liquid pipe 40. Becomes low pressure.
  • the switching valve 12 moves to the first end cover 19 side from the operation of the above-described subordinate four-way valve 1 to the state shown in FIG. 1, and the first pipe 4 and the fourth pipe 7 are connected to the valve chamber. 3, the second pipe 5 and the third pipe 6 communicate with each other via the folded flow path 11 a.
  • the high-pressure refrigerant vapor (point A) discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled by the outdoor air in the outdoor heat exchanger 25, which is a condenser, and condensed. Is done.
  • the condensed refrigerant liquid passes through the subordinate four-way valve 1 (point B) and then expands and accelerates while changing the isentropy at the nozzle 59 of the ejector 61 (point E).
  • the ejector pipe At the inlet of the diffuser 60, the ejector pipe
  • the refrigerant vapor (point D) that has passed through 62 is attracted and mixed (point F), and the pressure is recovered by the diffuser 60 (point G).
  • the refrigerant whose pressure has been recovered flows into the gas-liquid separator 32 in a gas-liquid two-phase state, and is separated into refrigerant vapor (point K) and refrigerant liquid (point H).
  • the separated refrigerant liquid is the first decompression device.
  • the refrigerant takes the heat from the indoor air by the indoor heat exchanger 26 as an evaporator, evaporates, passes through the main four-way valve 24 (point J), passes through the ejector pipe 62, and is ejected by the decompressor 63 for ejector.
  • the pressure is reduced (point D) and is attracted and mixed by the high-speed refrigerant (point E) that has passed through the nozzle 59 (point F). That is, the refrigerant flow rate circulating through the indoor heat exchanger 26 is all the flow rate attracted by the ejector 61.
  • the refrigerant vapor separated by the gas-liquid separator 32 flows into the compressor 23 through the gas-liquid separation return pipe 71 via the gas-liquid separation return flow valve 64 (point K).
  • the gas-liquid separator 32 When the air conditioner shown in Embodiment 6 is air-cooled, the gas-liquid separator 32 is provided. Therefore, the enthalpy difference (h3-h1) of the indoor heat exchanger 26 that is an evaporator is enthalpy of the conventional air conditioner. It becomes larger than the difference (h3 ⁇ h2). Therefore, the evaporation capacity, that is, the cooling capacity is increased as compared with the conventional example.
  • the ejector 61 is provided, so that the input of the compressor 23 is reduced by the pressure increase (P1-P2) due to the use of the ejector 61, The coefficient of performance during cooling operation obtained by dividing the evaporation capacity by the input of the compressor 23 is increased as compared with the conventional example. Further, since the ejector pipe 62 is provided, the refrigerant vapor evaporated by the indoor heat exchanger 26 is sucked by the ejector 61, and the refrigerant can be circulated through the indoor heat exchanger 26.
  • the shape of the pressure-enthalpy diagram when the heating operation is performed is almost equal to that in FIG.
  • the point B and the point C are interchanged.
  • the solenoid valve 43 is driven to switch the main four-way valve 24 so that the discharge side connection port 44 and the second connection port 47 communicate with each other and the suction side connection port 45 and the first connection port 46 communicate with each other.
  • the compressor 23 is driven, the third pipe 6 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the gas-liquid separation return pipe 71 and the gas pipe are connected to the suction side of the compressor 23.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicated via the liquid separator 32, the diffuser 60, the ejector pipe 62, the main four-way valve 24, the outdoor gas pipe 37, the outdoor heat exchanger 25, and the outdoor liquid pipe 38. Becomes low pressure. Therefore, the switching valve 12 moves to the second end cover 20 side from the operation of the subordinate four-way valve 1 described above to be in the state of FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor (point A) discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24 and is cooled by indoor air in the indoor heat exchanger 25 that is a condenser. , Condensed.
  • the condensed refrigerant liquid passes through the subordinate four-way valve 1 (point B), then expands and accelerates while changing the isentropy at the nozzle 59 (point E), and passes through the ejector pipe 62 at the inlet of the diffuser 60.
  • the refrigerant vapor (point D) is attracted and mixed (point F), and the pressure is restored by the diffuser 60 (point G).
  • the refrigerant whose pressure has been recovered flows into the gas-liquid separator 32 in a gas-liquid two-phase state, and is separated into refrigerant vapor (point K) and refrigerant liquid (point H).
  • the separated refrigerant liquid is the first decompression device.
  • the refrigerant evaporates by taking heat from the outside air in the outdoor heat exchanger 25 that is an evaporator, passes through the main four-way valve 24 (point J), passes through the ejector piping 62, and is decompressed by the ejector decompression device 63.
  • the high-speed refrigerant (point E) that has passed through the nozzle 59 is attracted and mixed (point F). That is, the refrigerant flow rate circulating through the outdoor heat exchanger 25 is all the flow rate attracted by the ejector 61.
  • the refrigerant vapor separated by the gas-liquid separator 32 flows into the compressor 23 through the gas-liquid separation return pipe 71 via the gas-liquid separation return flow valve 64 (point K).
  • the air conditioner shown in Embodiment 6 When the air conditioner shown in Embodiment 6 is operated for heating, since the ejector 61 is provided, the input to the compressor 23 is reduced by the pressure increase (P1-P2) due to the use of the ejector 61. Therefore, when the air conditioner is operated so that the condensing capacity is constant, the coefficient of performance during the heating operation obtained by dividing the condensing capacity by the input of the compressor 23 is increased as compared with the conventional example. Further, since the ejector pipe 62 is provided, the refrigerant vapor evaporated by the outdoor heat exchanger 25 is sucked by the ejector 61, and the refrigerant can be circulated through the outdoor heat exchanger 25.
  • the subordinate four-way valve 1 used in the air conditioner of the sixth embodiment has the configuration shown in FIGS. 1 and 2, and thus the subordinate four-way valve 1 was used for cooling operation and heating operation.
  • the switching valve 12 of the dependent four-way valve 1 can be automatically switched in response to a pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1. it can.
  • the decompression path 22 includes the first decompression device 30, the gas-liquid separator 32, and the ejector 61, and the subordinate four-way valve 1 is disposed at both ends of the decompression path 22.
  • the high-pressure refrigerant flows into the ejector 61, expands by isentropic change at the nozzle 59, and sucks the refrigerant vapor through the ejector pipe 62.
  • the pressure is recovered by the diffuser 60, it flows into the gas-liquid separator 32 in a gas-liquid two-phase state, and is further separated into the refrigerant vapor and the refrigerant liquid by the gas-liquid separator 32.
  • the ejector 61 and the gas-liquid separator 32 function such that the refrigerant is depressurized by the first pressure reducing device 30 after flowing out and the separated refrigerant vapor flows out through the gas-liquid separating return pipe 71. It is possible to form a flow of the refrigerant that operates urchin. Therefore, the coefficient of performance can be increased in both the cooling operation and the heating operation of the air conditioner.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21.
  • the fourth pipe 7 there is no shortcut from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the description of the reheat dehumidification operation is omitted, but the reheat dehumidification operation can be performed by making the configuration of the indoor heat exchanger 26 the same as in the first embodiment.
  • at least one of the first decompressor 30 and the ejector decompressor 63 may be deleted. In this case, the pressure loss from the liquid refrigerant outlet of the gas-liquid separator 32 to the sub four-way valve 1, the indoor heat exchanger 26 (or the outdoor heat exchanger 25), the main four-way valve 24, and the nozzle 59 is reduced.
  • the amount of refrigerant attracted by the high-speed refrigerant (point E) after passing through the nozzle 59 can be increased, and the heat exchange amount of the indoor heat exchanger 26 can be improved.
  • the gas-liquid separation return flow valve 64 may be deleted. In this case, since the pressure loss from the refrigerant vapor outlet of the gas-liquid separator 32 to the inlet of the compressor 23 can be reduced, the suction pressure of the compressor 23 is increased and the electric input of the compressor 23 is increased. Can be reduced.
  • the first pressure reducing device 30 By providing the first pressure reducing device 30 in the pressure reducing path 22, it is possible to adjust a pressure reducing amount that cannot be controlled by the ejector 61.
  • FIG. 17 is a refrigerant circuit diagram of an air conditioner according to Embodiment 7 of the present invention.
  • the air conditioner of the seventh embodiment is different from the first embodiment in that the decompression path 22 is not provided with the gas-liquid separator 32, and the first decompressor 30 and the first supercooling heat exchanger. 53 (provided downstream of the first decompressor 30), a second supercooling heat exchanger 65 (provided downstream of the first supercooling heat exchanger 53), and a second decompressor. 31 (provided on the downstream side of the second supercooling heat exchanger 65).
  • the main path includes the subordinate four-way valve 1 so that the flow direction of the refrigerant passing through the decompression path 22 is constant in both the cooling operation and the heating operation.
  • the refrigerant branched from the time until it reaches the second subcooling heat exchanger 65 downstream of the first subcooling heat exchanger 53 is returned to the intermediate compression process of the compressor 23.
  • a supercooling injection pipe 55 is provided.
  • the supercooling injection pipe 55 is provided with a supercooling decompression device 54 for setting the branched refrigerant to an intermediate pressure, and the refrigerant after passing through the supercooling decompression device 54 and the first decompression device 30.
  • each of the four-way valves 1 and 24 shows a state during cooling operation.
  • FIG. 18 is a pressure-enthalpy diagram, where the solid line indicates the operation of the refrigerant circuit of the air conditioner shown in the seventh embodiment, and the alternate long and short dash line (line connecting ABCA-DA) in FIG.
  • movement of the refrigerant circuit of the conventional air conditioner shown in FIG. A to L in the figure correspond to points A to L shown in FIG. 17 and FIG.
  • the air conditioner performs a cooling operation.
  • the operation of the conventional air conditioner is the same as the conventional operation shown in FIG. 6, and in FIG. 18, the inclination of the straight line from the C point to the D point is ignored.
  • the solenoid valve 43 is driven, the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47 are connected.
  • the main four-way valve 24 is switched so as to communicate with each other.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the third pipe of the subordinate four-way valve 1 communicating with the suction side of the compressor 23 is increased.
  • the pipe 6 has a low pressure.
  • the switching valve 12 moves to the first end cover 19 side from the operation of the dependent four-way valve 1 described above, and the state shown in FIG. 1 is established.
  • the second pipe 5 and the third pipe 6 communicate with each other via the return channel 11a.
  • the high-pressure refrigerant vapor (point E) discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled by the outdoor air in the outdoor heat exchanger 25, which is a condenser, and condensed. Is done. After the condensed refrigerant liquid passes through the subordinate four-way valve 1 (point B), it is depressurized by the first decompression device 30 (point F), and further flows through the first supercooling heat exchanger 53 in an opposite direction. It is cooled (point G) by a refrigerant with pressure P3 (points K to L).
  • the refrigerant is further cooled by a low-pressure P4 refrigerant (point J to point D) that flows oppositely in the second subcooling heat exchanger 65 (point H to point D), and then depressurized by the second decompression device 31 (I Point), the process proceeds to the indoor heat exchanger 26 via the dependent four-way valve 1.
  • the refrigerant takes the heat from the indoor air in the indoor heat exchanger 26 as an evaporator and evaporates, but does not completely evaporate and passes through the main four-way valve 24 in a gas-liquid two-phase state (point J).
  • the second supercooling heat exchanger 65 heat is removed from the refrigerant having the intermediate pressure P2 (G point to H point) and evaporated (D point), and the process proceeds to the compressor 23.
  • a part of the refrigerant liquid branched to the supercooling injection pipe 55 at the point G is decompressed to the intermediate pressure P3 by the supercooling decompression device 54 (point K), and then the first supercooling heat exchanger.
  • the heat is removed from the refrigerant (point F to point G) of the intermediate pressure P2 that flows in the opposite direction at 53 (point L), it does not evaporate completely, and the compressor 23 is in a gas-liquid two-phase state. It is injected halfway (point M), and the refrigerant at point L and the refrigerant at point M are mixed (point N). Further, the refrigerant is compressed to point E and discharged again.
  • the first subcooling heat exchanger 53 and the second subcooling heat exchanger 65 are provided, so the enthalpy difference of the indoor heat exchanger 26 that is an evaporator. (H3 ⁇ h1) becomes larger than the enthalpy difference (h4 ⁇ h2) of the conventional air conditioner. Therefore, the evaporation capacity, that is, the cooling capacity is increased as compared with the conventional example. Further, since the supercooling injection pipe 55 is provided, the flow rate of the refrigerant flowing through the compressor 23 is increased by the flow rate of the refrigerant injected from the supercooling injection pipe 55 into the compressor 23.
  • the input of the compressor 23 also increases, since the evaporation capacity is larger than that, the coefficient of performance during the cooling operation obtained by dividing the evaporation capacity by the input of the compressor 23 is increased as compared with the conventional example. Further, since the temperature when discharged from the compressor is lower than that of the conventional example, the reliability of the compressor is improved.
  • the shape of the pressure-enthalpy diagram when the heating operation is performed is almost equal to that in FIG. However, when heating the conventional air conditioner shown in FIG. 29, the points B and C are interchanged.
  • the solenoid valve 43 is driven to switch the main four-way valve 24 so that the discharge side connection port 44 and the second connection port 47 communicate with each other and the suction side connection port 45 and the first connection port 46 communicate with each other.
  • the compressor 23 is driven, the third pipe 6 of the subordinate four-way valve 1 that communicates with the discharge side of the compressor 23 becomes high pressure, while the fourth pipe of the subordinate four-way valve 1 that communicates with the suction side of the compressor 23.
  • the piping 7 becomes a low pressure.
  • the switching valve 12 moves to the second end cover 20 side from the operation of the subordinate four-way valve 1 described above to be in the state of FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor (point E) discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24 and is cooled by indoor air in the indoor heat exchanger 26 that is a condenser. , Condensed. After the condensed refrigerant liquid passes through the subordinate four-way valve 1 (point B), it is depressurized by the first decompression device 30 (point F), and further flows through the first supercooling heat exchanger 53 in an opposite direction. It is cooled (point G) by a refrigerant with pressure P3 (points K to L).
  • the refrigerant is further cooled by a low-pressure P4 refrigerant (point J to point D) that flows oppositely in the second subcooling heat exchanger 65 (point H to point D), and then depressurized by the second decompression device 31 (I Point), the process proceeds to the outdoor heat exchanger 25 via the subordinate four-way valve 1.
  • the refrigerant takes heat from the outside air in the outdoor heat exchanger 25 that is an evaporator and evaporates, but does not completely evaporate, and after passing through the main four-way valve 24 in the gas-liquid two-phase state (point J), the second In the supercooling heat exchanger 65, heat is taken from the refrigerant (G point to H point) at the intermediate pressure P2 to evaporate (D point), and the process proceeds to the compressor 23.
  • a part of the refrigerant liquid branched to the supercooling injection pipe 55 at the point G is decompressed to the intermediate pressure P3 by the supercooling decompression device 54 (point K), and then the first supercooling heat exchanger.
  • the heat is removed from the refrigerant (point F to point G) of the intermediate pressure P2 that flows in the opposite direction at 53 (point L), it does not evaporate completely, and the compressor 23 is in a gas-liquid two-phase state. It is injected halfway (point M), and the refrigerant at point L and the refrigerant at point M are mixed (point N). Further, the refrigerant is compressed to point E and discharged again.
  • the supercooling injection pipe 55 When the air conditioner shown in the seventh embodiment is operated for heating, the supercooling injection pipe 55 is provided. Therefore, the refrigerant flow rate flowing through the indoor heat exchanger 26 that is a condenser is changed from the supercooling injection pipe 55 to the compressor 23. It increases with the flow rate of the refrigerant injected into the tank. For this reason, the condensing capacity, that is, the heating capacity is increased as compared with the conventional example. Further, the flow rate of refrigerant flowing through the compressor 23 increases due to the flow rate of refrigerant injected into the compressor 23 from the supercooling injection pipe 55.
  • the input of the compressor 23 also increases, since the condensing capacity is larger than that, the coefficient of performance during the heating operation obtained by dividing the condensing capacity by the input of the compressor 23 is increased as compared with the conventional example. Further, since the temperature when discharged from the compressor is lower than that of the conventional example, the reliability of the compressor is improved.
  • the subordinate four-way valve 1 used in the air conditioner of the seventh embodiment has the configuration shown in FIGS. 1 and 2, and thus the subordinate four-way valve 1 was used for cooling operation and heating operation.
  • the switching valve 12 of the dependent four-way valve 1 can be automatically switched in response to a pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1. it can.
  • the decompression path 22 is routed through the first decompression device 30, the first supercooling heat exchanger 53, the second supercooling heat exchanger 65, and the first 2, the sub four-way valve 1 is connected to both ends of the pressure reducing path 22, and the first supercooling heat exchanger 53 is connected to the supercooling injection pipe in both the cooling operation and the heating operation.
  • the second subcooling heat exchanger 65 can exchange heat with the refrigerant passing through 55, and the second subcooling heat exchanger 65 can exchange heat with the refrigerant returning to the compressor. Therefore, ability and a coefficient of performance can be increased. Further, the reliability of the compressor 23 is improved.
  • the refrigerant flowing in the heat exchanger is caused to flow oppositely.
  • the heat exchange performance of the first subcooling heat exchanger 53 and the second subcooling heat exchanger 65 can be improved.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21.
  • the fourth pipe 7 there is no shortcut from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the structure of the 1st subcooling heat exchanger 53 and the 2nd subcooling heat exchanger 65 is arbitrary, and the refrigerant
  • the description of the reheat dehumidification operation is omitted, but the reheat dehumidification operation can be performed by making the configuration of the indoor heat exchanger 26 the same as in the first embodiment.
  • FIG. 19 is a refrigerant circuit diagram of an air conditioner according to Embodiment 8 of the present invention.
  • the air conditioner of the eighth embodiment does not include the gas-liquid separator 32, the injection flow control valve 33, and the injection pipe 36.
  • the expander 72, An expansion power transmission means 73, a sub compressor 74, an expansion bypass pipe 75, and an expansion flow control valve 76 are provided.
  • an expander 72 is connected between the first pressure reducing device 30 and the second pressure reducing device 31, and a sub compressor 74 is connected between the main four-way valve 24 and the suction side of the compressor 23, and the inflow
  • An expansion bypass pipe 75 is connected to the pipe 41 and the outflow pipe 42, and an expansion flow control valve 76 is arranged in the expansion bypass pipe 75.
  • the expander 72 and the sub-compressor 74 are connected by an expansion power transmission means 73 so that the expansion power recovered by the expander 72 is transmitted to the sub-compressor 74.
  • a reciprocating type, a rotary type, a scroll type, and the like are conceivable.
  • the decompression path 22 includes the first decompression device 30, the expander 72, and the second decompression apparatus 31, and the main path includes the subordinate four-way valve 1.
  • the flow direction of the refrigerant passing through is made constant.
  • the solid line arrows indicate the flow direction of the refrigerant during the cooling operation
  • the broken line arrows indicate the flow direction of the refrigerant during the heating operation.
  • each of the four-way valves 1 and 24 shows a state during cooling operation.
  • FIG. 20 is a pressure-enthalpy diagram, where the solid line indicates the operation of the refrigerant circuit of the air conditioner shown in the eighth embodiment, and the alternate long and short dash line (the line connecting ABCA-DA).
  • the case where the refrigerant is carbon dioxide is shown, and the high pressure side is in a supercritical state.
  • a to F in the figure correspond to points A to F shown in FIGS. 19 and 29.
  • the air conditioner performs a cooling operation.
  • the operation of the conventional air conditioner is the same as the conventional operation shown in FIG. 6, and in FIG. 20, the inclination of the straight line from the point C to the point D is ignored.
  • the solenoid valve 43 is driven, the discharge side connection port 44 and the first connection port 46 communicate, and the suction side connection port 45 and the second connection port 47.
  • the main four-way valve 24 is switched so as to communicate with each other. Further, the first decompressor 30 and the second decompressor 31 are fully opened, and the expansion flow control valve 76 is closed.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the third pipe of the subordinate four-way valve 1 communicating with the suction side of the compressor 23 is increased.
  • the pipe 6 has a low pressure.
  • the switching valve 12 moves to the first end cover 19 side from the operation of the dependent four-way valve 1 described above, and the state shown in FIG. 1 is established.
  • the second pipe 5 and the third pipe 6 communicate with each other via the return channel 11a.
  • the high-pressure refrigerant vapor (point A) discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled by the outdoor air in the outdoor heat exchanger 25, which is a radiator, to dissipate heat. Is done.
  • the radiated refrigerant flows through the dependent four-way valve 1 (point B) and then flows into the expander 72 through the first pressure reducing device 30.
  • the refrigerant is expanded by isentropic change while giving the energy of the refrigerant to the rotational motion or amplitude motion of the expander 72.
  • the rotational motion and the reciprocating motion of the expander 72 are transmitted to the sub compressor 74 via the expansion power transmission means 73, and the sub compressor 74 is driven.
  • the refrigerant that has passed through the expander 72 passes through the second pressure reducing device 31 (point E), then proceeds to the indoor heat exchanger 26 via the dependent four-way valve 1, and is indoors in the indoor heat exchanger 26 that is an evaporator. Removes heat from the air and evaporates.
  • the evaporated refrigerant vapor flows into the sub compressor 74 after passing through the main four-way valve 24 (D point).
  • the refrigerant flowing into the sub-compressor 74 is compressed to the point F, and further compressed to the point A by the compressor 23 and discharged again.
  • the expander 72 When the air conditioner shown in Embodiment 8 is in cooling operation, the expander 72 is provided, so that the enthalpy difference (h3-h1) of the indoor heat exchanger 26 that is an evaporator is equal to the enthalpy difference ( larger than h3-h2). Therefore, the evaporation capacity, that is, the cooling capacity is increased as compared with the conventional example. Further, since the refrigerant is compressed by the sub-compressor 74 using the expansion power obtained by the expander 72, the input of the compressor 23 is reduced, and the cooling operation obtained by dividing the evaporation capacity by the input of the compressor 23 is performed. The coefficient of performance increases compared to the conventional example.
  • the shape of the pressure-enthalpy diagram when the heating operation is performed is almost equal to that in FIG.
  • the points B and C are interchanged.
  • the solenoid valve 43 is driven to switch the main four-way valve 24 so that the discharge side connection port 44 and the second connection port 47 communicate with each other and the suction side connection port 45 and the first connection port 46 communicate with each other.
  • the first decompressor 30 and the second decompressor 31 are fully opened, and the expansion flow control valve 76 is closed.
  • the third pipe 6 of the subordinate four-way valve 1 that communicates with the discharge side of the compressor 23 becomes high pressure
  • the fourth pipe of the subordinate four-way valve 1 that communicates with the suction side of the compressor 23 becomes high pressure
  • the piping 7 becomes a low pressure. Therefore, the switching valve 12 moves to the second end cover 20 side from the operation of the subordinate four-way valve 1 described above to be in the state of FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor (point A) discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24 and is cooled by indoor air in the indoor heat exchanger 26 that is a radiator. The heat is dissipated.
  • the radiated refrigerant flows through the dependent four-way valve 1 (point B) and then flows into the expander 72 through the first pressure reducing device 30.
  • the expander 72 the refrigerant is expanded by isentropic change while giving the energy of the refrigerant to the rotational motion or amplitude motion of the expander 72.
  • the rotational motion and the reciprocating motion of the expander 72 are transmitted to the sub compressor 74 via the expansion power transmission means 73, and the sub compressor 74 is driven.
  • the refrigerant that has passed through the expander 72 passes through the second decompression device 31 (point E).
  • the process proceeds to the outdoor heat exchanger 25 via the subordinate four-way valve 1, and evaporates by taking heat from the outside air in the outdoor heat exchanger 25 that is an evaporator.
  • the evaporated refrigerant vapor flows into the sub compressor 74 after passing through the main four-way valve 24 (D point).
  • the refrigerant flowing into the sub-compressor 74 is compressed to the point F, and further compressed to the point A by the compressor 23 and discharged again.
  • Embodiment 8 When the air conditioner shown in Embodiment 8 is operated for heating, the refrigerant is compressed by the sub-compressor 74 using the expansion power obtained by the expander 72. Therefore, the input of the compressor 23 decreases, and the coefficient of performance at the time of heating operation obtained by dividing the heat radiation capacity by the input of the compressor 23 is increased as compared with the conventional example.
  • the subordinate four-way valve 1 used in the air conditioner of the eighth embodiment has the configuration shown in FIGS. 1 and 2, the subordinate four-way valve 1 is used for cooling as in the first embodiment.
  • the switching of the dependent four-way valve 1 is automatically performed in response to the pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1.
  • the valve 12 can be switched.
  • the air conditioner shown in the eighth embodiment includes the expander 72 in the decompression path 22 and the dependent four-way valve 1 connected to both ends of the decompression path 22, so that in either the cooling operation or the heating operation
  • the switching valve 12 of the subordinate four-way valve 1 by switching the switching valve 12 of the subordinate four-way valve 1, the refrigerant passing through the expander 72 flows into the expander 72 from the inflow pipe 41 and is expanded while changing the isentropy, and obtains expansion power.
  • a refrigerant flow in which the expander 72 functions can be formed. Therefore, the coefficient of performance can be increased in both the cooling operation and the heating operation of the air conditioner. Particularly in an air conditioner using carbon dioxide having a large pressure difference as a refrigerant, the effect of improving the coefficient of performance is large.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21.
  • the fourth pipe 7 there is no shortcut from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the first decompression device 30 and the second decompression device 31 are fully opened and decompressed by the expander 72 in both the cooling operation and the heating operation.
  • the air conditioner may be controlled by decompressing the refrigerant using the decompression device 30 or the second decompression device 31.
  • the expansion flow control valve 76 is closed in both the cooling operation and the heating operation.
  • the expansion flow control valve 76 may be adjusted so that the refrigerant flows through the expansion bypass pipe 75.
  • the pressure reducing operation in the pressure reducing path 22 is mainly performed in the expander 72, either the first pressure reducing device 30 or the second pressure reducing device 31 may be deleted. In addition, both may be deleted from the refrigerant circuit.
  • the description of the reheat dehumidification operation is omitted, but the reheat dehumidification operation can be performed by making the configuration of the indoor heat exchanger 26 the same as in the first embodiment.
  • the expander 72 and the sub compressor 74 may be configured in the same container, and the expander 72 and the sub compressor 27 may be configured integrally.
  • the compressor 23 and the sub compressor 74 may be configured in the same container, and the compressor 23 and the sub compressor 74 may be configured integrally.
  • the compressor 23, the sub-compressor 74, and the expander 72 may all be put in the same container, and the compressor 23, the sub-compressor 74, and the expander 72 may be configured integrally. Also good.
  • the sub compressor 74 may be disposed on the discharge side of the compressor 23. Further, the motor power of the compressor 23 may be reduced by connecting the expansion power transmission means 73 to the compressor 23 without using the sub compressor 74.
  • FIG. FIG. 21 is a refrigerant circuit diagram of an air conditioner according to Embodiment 9 of the present invention.
  • the decompression path 22 includes a gas-liquid separator 32 in addition to the configuration of the eighth embodiment. Further, an injection flow control valve 33 and an injection pipe 36 are provided.
  • the gas-liquid separator 32 is disposed downstream of the expander 72, and an injection pipe 36 connected to the gas-liquid separator 32 is configured to compress refrigerant vapor through the injection flow control valve 33 in the compression process of the compressor 32. It is connected to an injection port provided on the way.
  • each of the four-way valves 1 and 24 shows a state during cooling operation.
  • FIG. 22 is a pressure-enthalpy diagram, where the solid line indicates the operation of the refrigerant circuit of the air conditioner shown in the ninth embodiment, and the alternate long and short dash line (the line connecting ABCDA) is shown in FIG.
  • the case where the refrigerant is carbon dioxide is shown, and the high pressure side is in a supercritical state.
  • a to I and K in the figure correspond to points A to I and K shown in FIGS.
  • the air conditioner performs a cooling operation.
  • the operation of the conventional air conditioner is the same as the conventional operation shown in FIG. 6, and in FIG. 22, the inclination of the straight line from the C point to the D point is ignored.
  • the solenoid valve 43 is driven, the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47 are connected.
  • the main four-way valve 24 is switched so as to communicate with each other. Further, the first pressure reducing device 30 is fully opened, and the expansion flow control valve 76 is closed.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 becomes high pressure, while the third pipe of the subordinate four-way valve 1 communicating with the suction side of the compressor 23 is increased.
  • the pipe 6 has a low pressure.
  • the switching valve 12 moves to the first end cover 19 side from the operation of the dependent four-way valve 1 described above, and the state shown in FIG. 1 is established.
  • the second pipe 5 and the third pipe 6 communicate with each other via the return channel 11a.
  • the high-pressure refrigerant vapor (point E) discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled by the outdoor air in the outdoor heat exchanger 25, which is a radiator, to dissipate heat. Is done.
  • the radiated refrigerant flows through the dependent four-way valve 1 (point B) and then flows into the expander 72 through the first pressure reducing device 30.
  • the refrigerant is expanded by isentropic change while giving the energy of the refrigerant to the rotational motion or amplitude motion of the expander 72.
  • the rotational motion and the reciprocating motion of the expander 72 are transmitted to the sub compressor 74 via the expansion power transmission means 73, and the sub compressor 74 is driven.
  • the refrigerant that has passed through the expander 72 flows into the gas-liquid separator 32 in a gas-liquid two-phase state, and is separated into refrigerant vapor (point K) and refrigerant liquid (point G).
  • the separated refrigerant liquid (point G) is depressurized by the second decompression device 31 (point H), and then proceeds to the indoor heat exchanger 26 via the dependent four-way valve 1 to be an evaporator indoor heat exchanger. At 26, heat is taken from indoor air and evaporated.
  • the evaporated refrigerant vapor flows into the sub compressor 74 after passing through the main four-way valve 24 (D point).
  • the refrigerant that has flowed into the sub-compressor 74 is compressed to the point I, and further compressed to the point J by the compressor 23.
  • the flow rate of the intermediate-pressure refrigerant vapor (point K) separated by the gas-liquid separator 32 is adjusted by the injection flow control valve 33 and passes through the injection pipe 36 in the middle of the compression process of the compressor 23 (The refrigerant at point K is mixed with the refrigerant at point K and the refrigerant at point J (point L). Further, the refrigerant is compressed to point E and discharged again.
  • the expander 72 and the gas-liquid separator 32 are provided. Therefore, the enthalpy difference (h3 ⁇ h1) of the indoor heat exchanger 26 that is an evaporator is reduced by the conventional air. It becomes larger than the enthalpy difference (h3 ⁇ h2) of the harmonic machine. Therefore, the evaporation capacity, that is, the cooling capacity is increased as compared with the conventional example. Further, the refrigerant is compressed by the sub compressor 74 using the expansion power obtained by the expander 72. Therefore, the input of the compressor 23 decreases, and the coefficient of performance during the cooling operation obtained by dividing the evaporation capacity by the input of the compressor 23 increases compared to the conventional example. Further, since the injection pipe 36 is provided, the temperature (point E) when discharged from the compressor 23 is lower than that of the conventional example (point A), so that the reliability of the compressor 23 is improved.
  • the shape of the pressure-enthalpy diagram when the heating operation is performed is almost equal to that in FIG.
  • the points B and C are interchanged.
  • the solenoid valve 43 is driven to switch the main four-way valve 24 so that the discharge side connection port 44 and the second connection port 47 communicate with each other and the suction side connection port 45 and the first connection port 46 communicate with each other.
  • the first pressure reducing device 30 is fully opened, and the expansion flow control valve 76 is closed.
  • the third pipe 6 of the subordinate four-way valve 1 that communicates with the discharge side of the compressor 23 becomes high pressure
  • the fourth pipe of the subordinate four-way valve 1 that communicates with the suction side of the compressor 23 becomes high pressure
  • the piping 7 becomes a low pressure. Therefore, the switching valve 12 moves to the second end cover 20 side from the operation of the subordinate four-way valve 1 described above to be in the state of FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor (point E) discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24, and is cooled by indoor air in the indoor heat exchanger 26 that is a radiator. The heat is dissipated.
  • the radiated refrigerant flows through the dependent four-way valve 1 (point B) and then flows into the expander 72 through the first pressure reducing device 30.
  • the expander 72 the refrigerant is expanded by isentropic change while giving the energy of the refrigerant to the rotational motion or amplitude motion of the expander 72.
  • the rotational motion and the reciprocating motion of the expander 72 are transmitted to the sub compressor 74 via the expansion power transmission means 73, and the sub compressor 74 is driven.
  • the refrigerant that has passed through the expander 72 flows into the gas-liquid separator 32 in a gas-liquid two-phase state, and is separated into refrigerant vapor (point K) and refrigerant liquid (point G).
  • the separated refrigerant liquid (point G) is decompressed by the second decompression device 31 (point H), and then proceeds to the outdoor heat exchanger 25 via the dependent four-way valve 1 to be an evaporator outdoor heat exchanger. At 25, it takes heat from the outside air and evaporates.
  • the evaporated refrigerant vapor flows into the sub compressor 74 after passing through the main four-way valve 24 (D point).
  • the refrigerant flowing into the sub-compressor 74 is compressed to the point I and further compressed to the point J by the compressor 23.
  • the intermediate-pressure refrigerant vapor (point K) separated by the gas-liquid separator 32 is adjusted in flow rate by the injection flow control valve 33, passes through the injection pipe 36 and is in the middle of the compression process of the compressor 23 (
  • the refrigerant at point K) is mixed with the refrigerant at point K and the refrigerant at point J (point L). Further, the refrigerant is compressed to point E and discharged again.
  • Embodiment 9 When the air conditioner shown in Embodiment 9 is operated for heating, the refrigerant is compressed by the sub compressor 74 using the expansion power obtained by the expander 72. Therefore, the input of the compressor 23 decreases, and the coefficient of performance at the time of heating operation obtained by dividing the heat radiation capacity by the input of the compressor 23 is increased as compared with the conventional example. Moreover, since it has the injection piping 36, the temperature (E point) when discharging from a compressor falls rather than a prior art example (A point). Therefore, the reliability of the compressor is improved.
  • the subordinate four-way valve 1 used in the air conditioner of the ninth embodiment has the configuration shown in FIGS. 1 and 2, the subordinate four-way valve 1 is used for cooling as in the first embodiment.
  • the switching of the dependent four-way valve 1 is automatically performed in response to the pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1.
  • the valve 12 can be switched.
  • the air conditioner shown in the ninth embodiment includes the expander 72 and the gas-liquid separator 32 in the decompression path 22 and the subordinate four-way valve 1 connected to both ends of the decompression path 22, so that the cooling operation is performed.
  • the refrigerant passing through the expander 72 flows into the expander 72 from the inflow pipe 41 and is expanded while changing the isentropy.
  • the refrigerant flow in which the gas-liquid separator 32 functions can be formed. Therefore, the coefficient of performance can be increased in both the cooling operation and the heating operation of the air conditioner. Particularly in an air conditioner using carbon dioxide having a large pressure difference as a refrigerant, the effect of improving the coefficient of performance is large. Further, the reliability of the compressor 23 is improved.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21.
  • the fourth pipe 7 there is no shortcut from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the first decompression device 30 is fully opened and decompressed by the expander 72 in both the cooling operation and the heating operation.
  • the air conditioner may be controlled by reducing the pressure. Further, in the air conditioner of the ninth embodiment, the first pressure reducing device 30 may be deleted.
  • the expansion flow control valve 76 is closed in both the cooling operation and the heating operation. However, when the refrigeration cycle is not stable at the time of startup or the like, In cases where sufficient control cannot be achieved simply by passing the refrigerant, the expansion flow control valve 76 may be adjusted so that the refrigerant flows through the expansion bypass pipe 75.
  • the description of the reheat dehumidification operation is omitted, but the reheat dehumidification operation can be performed by making the configuration of the indoor heat exchanger 26 the same as in the first embodiment.
  • the expander 72 and the sub compressor 74 may be configured in the same container, and the expander 72 and the sub compressor 27 may be configured integrally.
  • the compressor 23 and the sub compressor 74 may be configured in the same container, and the compressor 23 and the sub compressor 74 may be configured integrally.
  • the compressor 23, the sub-compressor 74, and the expander 72 may all be put in the same container, and the compressor 23, the sub-compressor 74, and the expander 72 may be configured integrally. Also good.
  • the sub compressor 74 may be disposed on the discharge side of the compressor 23. Further, the motor power of the compressor 23 may be reduced by connecting the expansion power transmission means 73 to the compressor 23 without using the sub compressor 74.
  • gas-liquid separator 32 may be provided upstream of the expander 72 instead of being provided downstream of the expander 72.
  • FIG. FIG. 23 is a refrigerant circuit diagram of an air conditioner according to Embodiment 10 of the present invention.
  • the air conditioner of the tenth embodiment does not include the second decompression device 31, the gas-liquid separator 32, the injection pipe 36, and the injection flow control valve 33, and the decompression The path 22 includes only the first pressure reducing device 30.
  • the flow direction of the refrigerant passing through the decompression path 22 is constant in both the cooling operation and the heating operation.
  • the solid arrow indicates the refrigerant flow direction during the cooling operation
  • the broken arrow indicates the refrigerant flow direction during the heating operation.
  • each of the four-way valves 1 and 24 shows a state during cooling operation.
  • the solenoid valve 43 is driven so that the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47 communicate with each other. 24 is switched.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 is more than the third pipe 6 of the subordinate four-way valve 1 communicating with the suction side of the compressor 23. Pressure increases. For this reason, the switching valve 12 moves to the first end cover 19 side from the operation of the dependent four-way valve 1 described above, and the state shown in FIG. 1 is established.
  • the second pipe 5 and the third pipe 6 communicate with each other via the return channel 11a.
  • the high-pressure refrigerant vapor discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled and condensed by the outdoor air in the outdoor heat exchanger 25 that is a condenser.
  • the condensed refrigerant liquid is depressurized by the first pressure reducing device 30 after passing through the subordinate four-way valve 1, passes through the subordinate four-way valve 1, and then proceeds to the indoor heat exchanger 26 to exchange the indoor heat as an evaporator.
  • the vessel 26 evaporates by taking heat from indoor air.
  • the evaporated refrigerant vapor passes through the main four-way valve 24 and then proceeds to the compressor 23 where it is compressed and discharged again.
  • the solenoid valve 43 is driven so that the discharge side connection port 44 and the second connection port 47 communicate with each other, and the suction side connection port 45 and the first connection port 46 communicate with each other.
  • the four-way valve 24 is switched.
  • the third pipe 6 of the dependent four-way valve 1 communicating with the discharge side of the compressor 23 is more than the fourth pipe 7 of the dependent four-way valve 1 communicating with the suction side of the compressor 23.
  • Pressure increases. Therefore, the switching valve 12 moves to the first end cover 19 side from the operation of the subordinate four-way valve 1 described above and enters the state shown in FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24, and is cooled and condensed by indoor air in the indoor heat exchanger 26 that is a condenser. .
  • the condensed refrigerant liquid is reduced in pressure by the first pressure reducing device 30 after passing through the subordinate four-way valve 1, and again passes through the subordinate four-way valve 1, and then proceeds to the outdoor heat exchanger 25, where outdoor heat as an evaporator is obtained.
  • the exchanger 25 evaporates by taking heat from the outside air.
  • the evaporated refrigerant vapor passes through the main four-way valve 24 and then proceeds to the compressor 23 where it is compressed and discharged again.
  • the subordinate four-way valve 1 used in the air conditioner of the tenth embodiment has the configuration shown in FIGS. 1 and 2, the subordinate four-way valve 1 is used for cooling as in the first embodiment.
  • the switching of the dependent four-way valve 1 is automatically performed in response to the pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1.
  • the valve 12 can be switched. As a result, it is possible to reduce the number of solenoid valves used in the air conditioner, the control unit for operating the solenoid valves, and the wiring, so that the air conditioner can be made compact, and the control is simplified and the cost is reduced. Can be realized.
  • the flow direction of the refrigerant passing through the first pressure reducing device 30 is reversed between the cooling operation and the heating operation.
  • the decompression device 30 has directivity with respect to the flow direction of the refrigerant, and the accuracy of the decompression amount and the flow rate control amount of the decompression device 30 is deteriorated depending on the flow direction of the refrigerant.
  • the control performance of the decompression device 30 decreases and the lifetime of the device itself decreases.
  • the air conditioner shown in the tenth embodiment includes the dependent four-way valve 1 connected to both ends of the pressure reducing path 22, the first pressure reducing device 30 is provided for both the cooling operation and the heating operation.
  • the flow direction of the refrigerant passing therethrough can be made constant. Therefore, it is possible to satisfy the pressure reduction amount and the flow rate control amount of the first pressure reducing device 30, and it is possible to extend the structural life of the first pressure reducing device 30.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21.
  • the fourth pipe 7 there is no shortcut from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the description of the reheat dehumidification operation is omitted, but the reheat dehumidification operation can be performed by making the configuration of the indoor heat exchanger 26 the same as in the first embodiment.
  • FIG. 24 is a refrigerant circuit diagram of an air conditioner according to Embodiment 11 of the present invention.
  • the air conditioner of the eleventh embodiment is different from the tenth embodiment in that the outdoor liquid pipe connecting the first pressure reducing device 30 to the outdoor heat exchanger 25 and the fourth pipe 7 of the subordinate four-way valve 1. 38.
  • the indoor heat exchanger 26 is disposed between the inflow pipe 41 and the outflow pipe 42, one end of the indoor side gas pipe 39 is connected to the third pipe 6 of the subordinate four-way valve 1, and the subordinate four-way valve 1
  • the flow direction of the refrigerant passing through the indoor heat exchanger 26 is made constant.
  • the solid arrow indicates the refrigerant flow direction during the cooling operation
  • the broken arrow indicates the refrigerant flow direction during the heating operation.
  • each of the four-way valves 1 and 24 shows a state during cooling operation.
  • the solenoid valve 43 is driven so that the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47 communicate with each other. 24 is switched.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 is more than the third pipe 6 of the subordinate four-way valve 1 communicating with the suction side of the compressor 23. Pressure increases. For this reason, the switching valve 12 moves to the first end cover 19 side from the operation of the dependent four-way valve 1 described above, and the state shown in FIG. 1 is established.
  • the second pipe 5 and the third pipe 6 communicate with each other via the return channel 11a.
  • the high-pressure refrigerant vapor discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 via the main four-way valve 24, and is cooled and condensed by the outdoor air in the outdoor heat exchanger 25 that is a condenser.
  • the condensed refrigerant liquid is depressurized by the first pressure reducing device 30, passes through the subordinate four-way valve 1, proceeds to the indoor heat exchanger 26, and heats the indoor air by the indoor heat exchanger 26 that is an evaporator. Take away and evaporate.
  • the evaporated refrigerant vapor passes through the dependent four-way valve 1 and the main four-way valve 24 and then proceeds to the compressor 23 where it is compressed and discharged again.
  • the solenoid valve 43 is driven so that the discharge side connection port 44 and the second connection port 47 communicate with each other, and the suction side connection port 45 and the first connection port 46 communicate with each other.
  • the four-way valve 24 is switched.
  • the third pipe 6 of the dependent four-way valve 1 communicating with the discharge side of the compressor 23 is more than the fourth pipe 7 of the dependent four-way valve 1 communicating with the suction side of the compressor 23.
  • Pressure increases. Therefore, the switching valve 12 moves to the first end cover 19 side from the operation of the subordinate four-way valve 1 described above and enters the state shown in FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24 and the subordinate four-way valve 1, and is cooled by indoor air in the indoor heat exchanger 26 that is a condenser. And condensed.
  • the condensed refrigerant liquid is reduced in pressure by the first pressure reducing device 30 after passing through the subordinate four-way valve 1, proceeds to the outdoor heat exchanger 25, and takes heat from the outside air in the outdoor heat exchanger 25 that is an evaporator. Evaporate.
  • the evaporated refrigerant vapor passes through the main four-way valve 24 and then proceeds to the compressor 23 where it is compressed and discharged again.
  • the subordinate four-way valve 1 used in the air conditioner of the eleventh embodiment has the configuration shown in FIGS. 1 and 2, the subordinate four-way valve 1 is used for cooling as in the first embodiment.
  • the switching of the dependent four-way valve 1 is automatically performed in response to the pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1. Since the valve 12 can be switched, the number of solenoid valves used in the air conditioner, the control unit for operating the solenoid valves, and the wiring can be reduced, the air conditioner can be made compact, and the control Simplification and cost reduction can be realized.
  • the flow direction of the refrigerant passing through the indoor heat exchanger 104 is reversed between the cooling operation and the heating operation.
  • the air conditioner shown in the eleventh embodiment includes the dependent four-way valve 1 connected to both ends of the indoor heat exchanger 26, the flow direction of the refrigerant passing through the indoor heat exchanger 26 is constant.
  • 25 and 30 show the state of the end of a fin-and-tube heat exchanger 69 in which heat transfer tubes 68 are provided so as to be orthogonal to the fins 67 stacked in parallel as an example of the indoor heat exchanger.
  • FIG. 25 shows the state of the indoor heat exchanger 26 in the air conditioner of Embodiment 11, and FIG.
  • FIG. 30 shows the state of the indoor heat exchanger 104 in the conventional air conditioner.
  • a solid line arrow and a broken line arrow shown in each figure indicate the flow direction of the refrigerant passing through the U-turn portion of the heat transfer tube 68.
  • the solid line arrows indicate the flow direction of the refrigerant during the cooling operation, and the broken line arrows indicate the flow direction of the refrigerant during the heating operation.
  • the air flow direction 66 passing between the laminated fins 67 is blown in a certain direction by a fan or the like.
  • the refrigerant flows in from one heat transfer tube 68 located on the lower side of the heat exchanger, rises while making a U-turn at the end of the fin, turns back at the top, descends again while making a U-turn, and is located on the lower side. It flows out from the other heat transfer tube 68.
  • the heat exchanger is compared to the case of the parallel flow in which the refrigerant flows from the leeward heat transfer tube 68b to the leeward heat transfer tube 68a.
  • the heat transfer performance of 69 increases.
  • the flow direction of the refrigerant passing through the indoor heat exchanger 104 is reversed between the cooling operation and the heating operation. It becomes a parallel flow and the heat transfer performance of the heat exchanger decreases.
  • the flow direction of the refrigerant passing through the indoor heat exchanger 26 is constant in both the cooling operation and the heating operation. Therefore, as shown in FIG. 25, the flow of the refrigerant passing through the indoor heat exchanger 26 can be counterflowed in both the cooling operation and the heating operation. As a result, the heat transfer performance of the indoor heat exchanger 26 can be increased in both the cooling operation and the heating operation, and the cooling capacity and the heating capacity can be improved as compared with the conventional air conditioner.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21.
  • the fourth pipe 7 there is no shortcut from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the description of the reheat dehumidification operation is omitted, but the reheat dehumidification operation can be performed by making the configuration of the indoor heat exchanger 26 the same as in the first embodiment.
  • FIG. FIG. 26 is a refrigerant circuit diagram of an air conditioner according to Embodiment 12 of the present invention.
  • the air conditioner of the twelfth embodiment differs from the tenth embodiment in that an indoor side liquid pipe that connects the first decompressor 30 to the indoor heat exchanger 26 and the third pipe 6 of the subordinate four-way valve 1. 40.
  • the outdoor heat exchanger 25 is arranged between the inflow pipe 41 and the outflow pipe 42, one end of the outdoor gas pipe 37 is connected to the fourth pipe 7 of the subordinate four-way valve 1, and the subordinate four-way valve 1 In both the cooling operation and the heating operation, the flow direction of the refrigerant passing through the outdoor heat exchanger 25 is made constant.
  • each of the four-way valves 1 and 24 shows a state during cooling operation.
  • the solenoid valve 43 is driven so that the discharge side connection port 44 and the first connection port 46 communicate with each other, and the suction side connection port 45 and the second connection port 47 communicate with each other. 24 is switched.
  • the fourth pipe 7 of the subordinate four-way valve 1 communicating with the discharge side of the compressor 23 is more than the third pipe 6 of the subordinate four-way valve 1 communicating with the suction side of the compressor 23. Pressure increases. For this reason, the switching valve 12 moves to the first end cover 19 side from the operation of the dependent four-way valve 1 described above, and the state shown in FIG. 1 is established.
  • the second pipe 5 and the third pipe 6 communicate with each other via the return channel 11a.
  • the high-pressure refrigerant vapor discharged from the compressor 23 proceeds to the outdoor heat exchanger 25 through the main four-way valve 24 and the subordinate four-way valve 1, and is cooled by the outside air in the outdoor heat exchanger 25 that is a condenser. Condensed.
  • the condensed refrigerant liquid is reduced in pressure by the first pressure reducing device 30 after passing through the subordinate four-way valve 1, proceeds to the indoor heat exchanger 26, and heat is taken from indoor air by the indoor heat exchanger 26 that is an evaporator. Take away and evaporate.
  • the evaporated refrigerant vapor passes through the main four-way valve 24 and then proceeds to the compressor 23 where it is compressed and discharged again.
  • the solenoid valve 43 is driven so that the discharge side connection port 44 and the second connection port 47 communicate with each other, and the suction side connection port 45 and the first connection port 46 communicate with each other.
  • the four-way valve 24 is switched.
  • the third pipe 6 of the dependent four-way valve 1 communicating with the discharge side of the compressor 23 is more than the fourth pipe 7 of the dependent four-way valve 1 communicating with the suction side of the compressor 23.
  • Pressure increases. Therefore, the switching valve 12 moves to the first end cover 19 side from the operation of the subordinate four-way valve 1 described above and enters the state shown in FIG. 2, and the first pipe 4 and the third pipe 6 are connected to the valve chamber 3.
  • the second pipe 5 and the fourth pipe 7 communicate with each other via the folded flow path 11a.
  • the high-pressure refrigerant vapor discharged from the compressor 23 proceeds to the indoor heat exchanger 26 via the main four-way valve 24, and is cooled and condensed by indoor air in the indoor heat exchanger 26 that is a condenser. .
  • the condensed refrigerant liquid is depressurized by the first pressure reducing device 30, passes through the dependent four-way valve 1, proceeds to the outdoor heat exchanger 25, and takes heat from the outside air by the outdoor heat exchanger 25 that is an evaporator. Evaporate.
  • the evaporated refrigerant vapor passes through the dependent four-way valve 1 and the main four-way valve 24 and then proceeds to the compressor 23 where it is compressed and discharged again.
  • the subordinate four-way valve 1 used in the air conditioner of the twelfth embodiment has the configuration shown in FIGS. 1 and 2, the subordinate four-way valve 1 is used for cooling as in the first embodiment.
  • the switching of the dependent four-way valve 1 is automatically performed in response to the pressure difference between the third pipe 6 and the fourth pipe 7 without using an electromagnetic valve that controls only the dependent four-way valve 1. Since the valve 12 can be switched, the number of solenoid valves used in the air conditioner, the control unit for operating the solenoid valves, and the wiring can be reduced, the air conditioner can be made compact, and the control Simplification and cost reduction can be realized.
  • the flow of the refrigerant passing through the outdoor heat exchanger 25 can be counterflowed in both the cooling operation and the heating operation.
  • the heat transfer performance of the outdoor heat exchanger 25 can be increased in both the cooling operation and the heating operation, and the cooling capacity and the heating capacity can be improved as compared with the conventional air conditioner.
  • the pressure in the valve chamber 3 of the subordinate four-way valve 1 becomes higher than the pressure in the return flow path 11a, and the valve body 11 is strongly pressed against the valve seat 21.
  • the fourth pipe 7 there is no shortcut from the fourth pipe 7 to the second pipe 5 in the dependent four-way valve 1, and a refrigerant circuit for performing a desired operation can be formed.
  • the description of the reheat dehumidifying operation is omitted, but the reheat dehumidifying operation can be performed by making the configuration of the outdoor heat exchanger 25 the same as in the first embodiment.
  • the first pipe 15 connected to the first cylinder chamber 13 of the subordinate four-way valve 1 is connected to the third pipe 6 and the second cylinder.
  • the second conduit 16 connected to the chamber 14 is connected to the fourth pipe 7, even if the flow direction of the fluid flowing through the main path is switched by the main four-way valve 24, the switching valve 12 of the subordinate four-way valve 1 is If it is possible to operate so that the fluid always flows in the same direction in the refrigerant path connected at both ends to the subordinate four-way valve 1, the first conduit 15 and the second conduit 16 are connected to the third pipe 6 and It is not necessary to connect to the fourth pipe 7.
  • the first conduit 15 and the second conduit 16 are respectively connected to two points where the pressure of the fluid is different and the magnitude relationship of the pressure is reversed by switching by the main four-way valve 24.
  • a part of the fluid flowing through the two points may be connected and the first conduit 15 and the second conduit 16 may be used to drive the valve body.
  • the main four-way valve 24 has a pair of conduits that are switched between high pressure and low pressure by the operation of the electromagnetic valve 43, the first conduit 15 is located at a position where one of the pair of conduits is connected.
  • the second conduit 16 may be connected to the position where the other conduit is connected.
  • the pressure in the valve chamber 3 is made larger than the pressure in the folded flow path 11a so as to press the valve body 11 against the valve seat 21.
  • the first pipe 4 has an inflow pipe 41
  • the second pipe 5 has an outflow pipe 42
  • the third pipe 6 has an indoor side liquid pipe 40 or an indoor side gas pipe 39
  • the fourth pipe 7 has an outdoor side liquid pipe 38.
  • the combination of the four connecting portions connecting the subordinate four-way valve 1 and the refrigerant circuit is limited to the above combination. Absent. For example, as shown in FIG.
  • the structure of the subordinate four-way valve 1 that does not require the valve body 11 to be pressed against the valve seat 21 does not include the piston shaft 10, and the valve body 11 includes the first piston 8 and the second piston 8.
  • the switching valve 12 is formed by being joined to the piston 9, and the valve body 11 is in close contact with the valve seat 21 and the four-way valve main body 2, and the first pipe 4 to the third pipe 6 or the third pipe 6 are connected to the valve body 11. It is good also as a structure which provided the 1st communicating path 77 and the 2nd communicating path 78 which connect selectively from the 1 piping 4 to the 4th piping 7.
  • FIG. By adopting such a configuration, the switching valve 12 is stably stabilized by the pressure difference between the first cylinder chamber 13 and the second cylinder chamber 14 like the subordinate four-way valve shown in FIGS. Slide in 2.
  • the outdoor heat exchanger 25 and the indoor heat exchanger 26 may be interchanged and connected, and the main four-way valve 24 and the subordinate are determined so as to determine the flow direction of the refrigerant in accordance with the refrigerant circuit after the exchange.
  • the four-way valve 1 may be switched.
  • the heat exchanger provided in the refrigerant circuit is the outdoor heat exchanger 25 and the indoor heat exchanger 26, both may be any heat exchanger that can exchange heat between the refrigerant passing through the refrigerant circuit, and the structure thereof is arbitrary. It is.
  • the medium in which the refrigerant exchanges heat is arbitrary, and air or water may be used.
  • the throttle amount of the first decompressor 30 and the throttle amount of the second decompressor 31 are arbitrary, and each of the cooling operation and the heating operation of the air conditioner can be performed by using a decompressor having a variable valve opening. In operation, the optimum operation that maximizes the coefficient of performance is possible.
  • the structure of the compressor 23 is arbitrary, and a refrigerant may be injected between the front stage and the rear stage as a two-stage compressor of the front stage and the rear stage.
  • chlorofluorocarbon natural refrigerants such as carbon dioxide and hydrocarbons
  • carbon dioxide which is a high-pressure refrigerant
  • it becomes a supercritical refrigeration cycle with a large compressor work when carbon dioxide, which is a high-pressure refrigerant, is used in a conventional air conditioner, it becomes a supercritical refrigeration cycle with a large compressor work.
  • a cooling operation is performed.
  • the coefficient of performance of the heating operation can be improved.
  • the indoor heat exchanger 26 (at the time of cooling operation) or the outdoor heat exchanger 25 (at the time of heating operation) is used.
  • the enthalpy of the refrigerant flowing in is smaller than that of the conventional example shown in FIG. 29, and the amount of refrigerant vapor is small.
  • the pressure loss of the indoor heat exchanger 26 (during cooling operation) or the outdoor heat exchanger 25 (during heating operation) decreases and the suction pressure of the compressor 23 increases, so that in either the cooling operation or the heating operation.
  • one main four-way valve 24 for switching the flow direction of the main path by driving the valve body using electric power of an electromagnetic valve or the like, the pressure reducing path 22, the outdoor heat exchanger 25, the refrigerant circuit in which one dependent four-way valve 1 is provided so that the direction of the refrigerant flowing into any one of the indoor heat exchangers 26 is a constant direction is shown.
  • the number of valves 1 and the number of main four-way valves 24 are arbitrary. In that case, the valve body of the subordinate four-way valve is driven not by electric power but by the pressure change generated in the main path by switching by the main four-way valve, and the flow direction switched by the main four-way valve 24 is locally at a desired position.
  • the configuration of the refrigerant circuit is not limited to the refrigerant circuit of each of the embodiments.
  • the switching means corresponding to the subordinate four-way valve 1 is not limited to the four-way valve, and the flow direction of the refrigerant can be switched without using an electromagnetic valve or the like.
  • the number of flow paths to be switched is arbitrary as long as it is a subordinate switching unit that can form a refrigerant circuit so that the air conditioner can be operated.
  • the air conditioner has been described.
  • the present invention is not limited to the air conditioner, and the same configuration can be applied to a refrigeration cycle apparatus that performs heating and cooling using a refrigerant.

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

Abstract

L'invention porte sur un dispositif de cycle de réfrigération qui a une dimension compacte et qui est commandé de façon simple. Ceci est obtenu par réduction du nombre de dispositifs d'entraînement pour entraîner des moyens de commutation pour une commutation entre les directions d'écoulement de fluide. L'invention porte également sur une vanne à quatre voies qui ne nécessite pas de dispositif d'entraînement. Le dispositif de cycle de réfrigération comporte un trajet principal formé par l'interconnexion, à l'aide d'une tuyauterie, d'un compresseur (23), d'un premier échangeur de chaleur (25), d'un trajet de réduction de pression (22) et d'un second échangeur de chaleur (26) ; une vanne à quatre voies principales (24) pour une commutation, par déplacement de la position d'un élément de vanne, entre les trajets d'écoulement internes pour changer la direction d'écoulement de fluide s'écoulant dans le trajet principal ; et une vanne à quatre voies dépendantes (1) pour une commutation, par déplacement de la position d'un élément de vanne, entre des trajets d'écoulement interne pour changer localement la direction d'écoulement modifiée par la vanne à quatre voies principales (24). L'élément de vanne de la vanne à quatre voies principales (24) est actionné électriquement, et l'élément de vanne de la vanne à quatre voies dépendantes (1) est entraîné par un changement de pression produit dans le trajet principal par commutation entre les directions d'écoulement par la vanne à quatre voies principales (24).
PCT/JP2008/003941 2008-01-07 2008-12-25 Dispositif de cycle de réfrigération et vanne à quatre voies Ceased WO2009087733A1 (fr)

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JP2010085022A (ja) * 2008-09-30 2010-04-15 Daikin Ind Ltd 冷凍装置
WO2011045977A1 (fr) * 2009-10-14 2011-04-21 株式会社 日立製作所 Climatiseur
JP2012093051A (ja) * 2010-10-28 2012-05-17 Fuji Koki Corp ヒートポンプ用気液分離器及びインジェクション式ヒートポンプシステム
CN102753915A (zh) * 2010-02-24 2012-10-24 株式会社日立制作所 空调装置
JP2012211688A (ja) * 2011-03-24 2012-11-01 Fujitsu General Ltd 四方弁とそれを備えたヒートポンプ装置
JP2012233676A (ja) * 2011-04-21 2012-11-29 Denso Corp ヒートポンプサイクル
CN103032999A (zh) * 2011-10-08 2013-04-10 陈则韶 用双四通阀切换的双热源热泵热水一体机
JP2013134040A (ja) * 2011-12-27 2013-07-08 Daikin Industries Ltd 冷凍装置
JP2014211293A (ja) * 2013-04-19 2014-11-13 ダイキン工業株式会社 冷凍装置
JP2018523085A (ja) * 2015-08-14 2018-08-16 ダンフォス アクチ−セルスカブ 少なくとも２つの蒸発器群を有する蒸気圧縮システム
CN109186129A (zh) * 2018-08-23 2019-01-11 珠海格力电器股份有限公司 热泵系统及热泵系统控制方法
JP2019158308A (ja) * 2018-03-16 2019-09-19 三菱電機株式会社 冷凍サイクル装置
CN110686424A (zh) * 2019-10-23 2020-01-14 陈希禄 一种储能空调
CN110953381A (zh) * 2019-12-27 2020-04-03 山前（珠海）医疗科技有限公司 一种三通阀及冷冻消融装置
WO2020156101A1 (fr) * 2019-01-31 2020-08-06 日立江森自控空调有限公司 Dispositif de distribution et de réglage de fluide frigorigène, système de climatisation et procédé de commande de système de climatisation
JP2021508025A (ja) * 2017-12-29 2021-02-25 青島海尓空調器有限総公司Ｑｉｎｇｄａｏ Ｈａｉｅｒ Ａｉｒ Ｃｏｎｄｉｔｉｏｎｅｒ Ｇｅｎｅｒａｌ Ｃｏｒｐ．，Ｌｔｄ． 空調機システム
CN113175768A (zh) * 2021-02-09 2021-07-27 三花控股集团有限公司 流体控制组件
WO2021220486A1 (fr) * 2020-04-30 2021-11-04 三菱電機株式会社 Dispositif à cycle de réfrigération
JP2022509452A (ja) * 2018-10-26 2022-01-20 トゥルボアルゴール ソチエタ ア レスポンサビリタ リミタータ 冷凍装置及びその操作方法
CN114072623A (zh) * 2019-07-16 2022-02-18 三菱电机株式会社 制冷循环装置
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