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WO2012147290A1 - Séparateur de gaz-liquide et appareil à cycle de réfrigération équipé du séparateur de gaz-liquide - Google Patents

Séparateur de gaz-liquide et appareil à cycle de réfrigération équipé du séparateur de gaz-liquide Download PDF

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Publication number
WO2012147290A1
WO2012147290A1 PCT/JP2012/002497 JP2012002497W WO2012147290A1 WO 2012147290 A1 WO2012147290 A1 WO 2012147290A1 JP 2012002497 W JP2012002497 W JP 2012002497W WO 2012147290 A1 WO2012147290 A1 WO 2012147290A1
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WIPO (PCT)
Prior art keywords
pipe
gas
refrigerant
liquid
liquid separator
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/JP2012/002497
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English (en)
Japanese (ja)
Inventor
浩昭 中宗
寿守務 吉村
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2013511902A priority Critical patent/JP5634597B2/ja
Publication of WO2012147290A1 publication Critical patent/WO2012147290A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

Definitions

  • the present invention relates to a gas-liquid separator that separates a gas-liquid two-phase fluid (for example, a refrigerant) into a gas-phase fluid and a liquid-phase fluid, and a refrigeration cycle apparatus equipped with the gas-liquid separator.
  • a gas-liquid separator that separates a gas-liquid two-phase fluid (for example, a refrigerant) into a gas-phase fluid and a liquid-phase fluid
  • a refrigeration cycle apparatus equipped with the gas-liquid separator.
  • compressed gas refrigerant is compressed in a refrigeration cycle in which a compressor, a four-way valve, an outdoor heat exchanger, a bridge circuit, an expansion valve, a gas-liquid separator, and an indoor heat exchanger are sequentially connected by piping.
  • a compressor, a four-way valve, an outdoor heat exchanger, a bridge circuit, an expansion valve, a gas-liquid separator, and an indoor heat exchanger are sequentially connected by piping.
  • the gas-liquid separator described in Patent Document 1 includes a first container to which an inflow pipe is connected, a second container to which an outflow pipe for liquid refrigerant is connected to the lower part, and an outflow pipe for gas refrigerant to the upper part. It has.
  • a pipe for allowing the gas refrigerant to pass therethrough is provided in the upper part of the first container and the upper part of the second container, and the liquid refrigerant is passed through the lower part of the first container and the lower part of the second container. Piping is provided.
  • gas-liquid separation is performed by reducing the refrigerant speed in the gas-liquid two-phase state that has flowed in the first container, or the gas-liquid two in a foamed state is used.
  • the bubbled refrigerant vapor is floated from the phase refrigerant and separated into gas and liquid, so that the diameter of the first container needs to be considerably larger than the diameter of the inflow pipe, and the gas-liquid separator becomes larger. was there.
  • the present invention addresses the above-described problems, and provides a gas-liquid separator that has a high gas-liquid separation efficiency and is miniaturized, and a refrigeration cycle apparatus equipped with the gas-liquid separator. Objective.
  • the gas-liquid separator includes a first pipe, a second pipe, an upper pipe connecting the upper part of the first pipe and the upper part of the second pipe, a lower part of the first pipe, and the first pipe.
  • a lower pipe that connects the lower part of the two pipes, a fluid inflow pipe that allows a gas-liquid two-phase fluid to flow into the first pipe, and a gas phase fluid outflow that is connected to the upper pipe and flows out the gas phase fluid
  • the fluid inflow pipe has an end portion (hereinafter referred to as an outflow side end portion) on the side where an outflow portion for flowing out the gas-liquid two-phase fluid is inserted into the first pipe, and the outflow portion Is a gas-liquid two-phase fluid that has flowed into the first pipe. Are those formed to impinge on.
  • the refrigeration cycle apparatus according to the present invention is equipped with the gas-liquid separator according to the present invention, and uses a refrigerant as the fluid.
  • the gas-liquid two-phase refrigerant can be separated with high gas-liquid separation efficiency, and it can be configured only by piping having no container. Therefore, according to the present invention, it is possible to provide a gas-liquid separator that can greatly reduce the manufacturing cost, and that can be reduced in size and thickness, and a refrigeration cycle apparatus equipped with the gas-liquid separator. can do.
  • FIG. 1 is a structural diagram of a gas-liquid separator 5 according to Embodiment 1 of the present invention. It is a Mollier diagram which shows the relationship between the enthalpy and pressure in the refrigeration cycle apparatus which mounts the gas-liquid separator 5 which concerns on Embodiment 1 of this invention, and the refrigeration cycle apparatus which does not mount a gas-liquid separator. It is an example of the block diagram of the refrigerating-cycle apparatus which does not mount a gas-liquid separator.
  • FIG. 1 is a configuration diagram of a refrigeration cycle apparatus equipped with a gas-liquid separator 5 according to Embodiment 1 of the present invention.
  • the refrigeration cycle apparatus according to Embodiment 1 includes at least a compressor 1, a four-way valve 2, a heat source side first heat exchanger 3, an expansion valve 4, a gas-liquid separator 5, and a use side second heat exchanger. 6, the compressor 1, the four-way valve 2, the first heat exchanger 3, the expansion valve 4, the gas-liquid separator 5, the second heat exchanger 6, the four-way valve 2, and the compressor 1 in this order. It is connected by refrigerant piping and constitutes the main circuit of the refrigeration cycle circuit (refrigerant circuit).
  • a bypass circuit 10 is configured that connects a gas refrigerant outflow pipe 16 described later to a refrigerant pipe that connects the second heat exchanger 6 and the four-way valve 2.
  • the bypass circuit 10 includes an electromagnetic valve 7, a check valve 8, and a capillary tube 9.
  • the gas refrigerant outlet pipe 16 is connected in the order of the electromagnetic valve 7, the check valve 8, and the capillary tube 9.
  • the order is not limited to this, and any order is possible. But you can. If only the refrigerant does not flow through the bypass circuit 10 in the heating operation of the refrigeration cycle apparatus described later, only the check valve 8 may be used without using the electromagnetic valve 7.
  • the electromagnetic valve 7 is closed when it is not necessary to operate the gas-liquid separator 5 in the cooling operation.
  • the solenoid valve 7 and the check valve 8 may be installed depending on whether or not the gas-liquid separator is operated in the air conditioning operation.
  • the gas refrigerant 20d flowing out of the gas-liquid separator 5 from the gas refrigerant outflow pipe 16 may be returned to the suction side of the compressor 1, so that the bypass circuit 10 is connected to the compressor 1 as shown in FIG. It may be connected between the four-way valves 2.
  • Compressor 1 compresses the sucked gas refrigerant and discharges the high-temperature and high-pressure gas refrigerant.
  • the four-way valve 2 has a function of switching the flow path of the gaseous refrigerant discharged from the compressor 1.
  • the four-way valve 2 switches the flow path so that the gaseous refrigerant discharged from the compressor 1 flows into the first heat exchanger 3.
  • the four-way valve 2 switches the flow path so that the gaseous refrigerant discharged from the compressor 1 flows into the second heat exchanger 6.
  • the first heat exchanger 3 is provided with a fan in the vicinity thereof for exchanging heat between the outside air and the like and the refrigerant circulating inside.
  • the first heat exchanger 3 includes the high-temperature and high-pressure gas refrigerant discharged from the compressor 1, the outside air sent by the fan, and the like. Heat exchange is performed and the gaseous refrigerant is condensed.
  • the first heat exchanger 3 performs heat exchange between the low-temperature and low-pressure refrigerant sent from the expansion valve 4 and the outside air or the like sent by the fan, Evaporate.
  • the expansion valve 4 expands and decompresses the incoming liquid refrigerant, and flows out as a low-temperature and low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid separator 5 separates the flowing gas-liquid two-phase refrigerant into liquid refrigerant and gas refrigerant. Details of the configuration and operation of the gas-liquid separator 5 will be described later.
  • the second heat exchanger 6 is provided with a fan in the vicinity thereof for exchanging heat between indoor air and the like and refrigerant circulating in the interior.
  • the second heat exchanger 6 includes a low-temperature and low-pressure liquid refrigerant separated from the gas-liquid two-phase refrigerant by the gas-liquid separator 5 and a fan. It exchanges heat with the indoor air that is sent, and evaporates the low-temperature and low-pressure liquid refrigerant.
  • the second heat exchanger 6 performs heat exchange between the high-temperature and high-pressure gas refrigerant discharged from the compressor 1 and the outside air or the like sent by the fan, and the gas refrigerant. To condense.
  • the solenoid valve 7 When the cooling operation is performed by the refrigeration cycle apparatus according to the first embodiment, the solenoid valve 7 is opened, and the gas refrigerant separated from the gas-liquid two-phase refrigerant by the gas-liquid separator 5 is supplied to the bypass circuit 10. Circulate. Further, when the heating operation is performed by the refrigeration cycle apparatus according to the first embodiment, the solenoid valve 7 is closed so that the refrigerant does not flow through the bypass circuit 10.
  • the check valve 8 circulates the refrigerant in only one direction in the bypass circuit 10, and specifically circulates the refrigerant in the direction from the gas-liquid separator 5 to the compressor 1.
  • the capillary tube 9 is a capillary tube made of copper or the like, and adjusts the flow rate of the gaseous refrigerant to be circulated through the bypass circuit 10.
  • An expansion valve may be used as a means for adjusting the flow rate.
  • the expansion valve 4 corresponds to “expansion means” in the present invention.
  • FIG. 2 is a structural diagram of the gas-liquid separator 5 according to Embodiment 1 of the present invention.
  • the gas-liquid separator 5 according to the first embodiment is arranged in a substantially vertical direction as well as a first vertical pipe 11 as a first refrigerant flow path arranged in a substantially vertical direction.
  • the second vertical pipe 12 as the second refrigerant flow path
  • the upper pipe 13 as a connecting portion connecting the upper end of the first vertical pipe 11 and the upper end of the second vertical pipe 12
  • the first vertical pipe A lower pipe 14 is provided as a connecting part that connects the lower end of the pipe 11 and the lower end of the second vertical pipe 12.
  • the first vertical pipe 11, the second vertical pipe 12, the upper pipe 13 and the lower pipe 14 form a loop pipe 30.
  • the gas-liquid separator 5 includes a gas refrigerant outflow pipe 16 connected to an upper pipe 13 (more specifically, a junction between the second vertical pipe 12 and the upper pipe 13), and a lower part.
  • a liquid refrigerant outflow pipe 17 connected to the pipe 14 (more specifically, the junction of the second vertical pipe 12 and the lower pipe 14) is provided.
  • the gas refrigerant outflow pipe 16 extends upward from the upper pipe 13, and the liquid refrigerant outflow pipe 17 extends downward from the lower pipe 14.
  • the gas-liquid separator 5 includes the refrigerant inflow pipe 15 in which one end (hereinafter referred to as the outflow side end 15a) is inserted into the first vertical pipe 11.
  • An outflow portion 50 through which the gas-liquid two-phase refrigerant flowing into the refrigerant inflow piping 15 flows out is formed at the outflow side end portion 15a of the refrigerant inflow piping 15.
  • the opening at the front end of the outflow side end portion 15a is used as the outflow portion 50 as it is.
  • coolant inflow piping 15 which concerns on this Embodiment 1 is bent so that the outflow side edge part 15a may face the inner wall of the 1st vertical piping 11. As shown in FIG.
  • the upper pipe 13 is a refrigerant pipe that joins the gas refrigerant 20a rising in the first vertical pipe 11 with the gas refrigerant 20c rising in the second vertical pipe 12, as will be described later. Further, the upper pipe 13 is located outside the loop pipe 30 between the upper end portion of the first vertical pipe 11 and the upper end portion of the second vertical pipe 12 positioned above the upper end portion of the first vertical pipe 11. It forms so that it may become circular arc shape toward.
  • the lower pipe 14 is a refrigerant pipe for sending the liquid refrigerant 21b descending in the first vertical pipe 11 to the second vertical pipe 12 and the liquid refrigerant outflow pipe 17, as will be described later. Further, the lower pipe 14 is located outside the loop pipe 30 between the lower end of the first vertical pipe 11 and the lower end of the second vertical pipe 12 positioned below the lower end of the first vertical pipe 11. It forms so that it may become circular arc shape toward.
  • the tip of the outflow side end 15a of the refrigerant inflow pipe 15 is inserted between the uppermost point and the lowermost point of the loop-shaped pipe 30 at a position having a ratio of H1: H2 in the vertical direction.
  • the distance H1 only needs to be sufficiently high in the gas-liquid separation of the gas-liquid two-phase refrigerant, and the ratio of H1: H2 is not limited, but is, for example, about 2: 1 to 3: 1. Should be set.
  • the first vertical pipe 11 and the second vertical pipe 12 correspond to “first pipe” and “second pipe” in the present invention, respectively.
  • the refrigerant inflow piping 15, the gas refrigerant outflow piping 16, and the liquid refrigerant outflow piping 17 correspond to the “fluid inflow piping”, “gas phase fluid outflow piping”, and “liquid phase fluid outflow piping” in the present invention, respectively.
  • FIG. 3 is a Mollier line showing the relationship between enthalpy and pressure in a refrigeration cycle apparatus equipped with the gas-liquid separator 5 according to Embodiment 1 of the present invention and a refrigeration cycle apparatus not equipped with a gas-liquid separator.
  • FIG. 4 is an example of a configuration diagram of a refrigeration cycle apparatus not equipped with a gas-liquid separator.
  • the solid line shows the relationship between the enthalpy and pressure of the refrigeration cycle apparatus equipped with the gas-liquid separator 5
  • the broken line shows the refrigeration cycle apparatus shown in FIG. 4 without the gas-liquid separator.
  • FIG. 3 correspond to the refrigerant states at the positions indicated by points A to F in the refrigeration cycle apparatus (FIG. 1) according to the first embodiment. Further, the refrigerant states indicated by points A to C and D ′ in FIG. 3 correspond to the refrigerant states at the positions indicated by points A to C and D ′ in the refrigeration cycle apparatus shown in FIG.
  • an air conditioner is used as an example of the refrigeration cycle apparatus
  • the first heat exchanger 3 on the heat source side functions as an outdoor heat exchanger
  • the second heat exchanger 6 on the use side functions as an indoor heat exchanger.
  • the operation when the refrigeration cycle apparatus not equipped with the gas-liquid separator shown in FIG. 4 performs the cooling operation will be described with reference to FIGS. 3 and 4.
  • the high-temperature and high-pressure gaseous refrigerant compressed and discharged by the compressor 1 passes through the four-way valve 2 to the first heat exchanger. 3 (point A).
  • the gaseous refrigerant that has flowed into the first heat exchanger 3 undergoes heat exchange with the outside air, condenses, becomes liquid refrigerant, and flows out from the first heat exchanger 3.
  • the gas-liquid two-phase refrigerant (point C) after passing through the expansion valve 4 is the second heat exchanger 6. Therefore, the pressure loss when the refrigerant passes through the second heat exchanger 6 becomes large (corresponding to (PC-PD ′) in FIG. 3).
  • the refrigeration cycle apparatus opens the solenoid valve 7 so that the refrigerant flows through the bypass circuit 10.
  • the high-temperature and high-pressure gaseous refrigerant compressed and discharged by the compressor 1 flows into the first heat exchanger 3 via the four-way valve 2 (point A).
  • the gaseous refrigerant that has flowed into the first heat exchanger 3 undergoes heat exchange with the outside air, condenses, becomes liquid refrigerant, and flows out of the first heat exchanger 3.
  • the liquid refrigerant (point B) flowing out from the first heat exchanger 3 flows into the expansion valve 4 and is expanded and depressurized by the expansion valve 4 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant.
  • This gas-liquid two-phase refrigerant (point C) flows into the gas-liquid separator 5.
  • the gas-liquid separation operation of the gas-liquid two-phase refrigerant by the gas-liquid separator 5 will be described in detail.
  • the gas-liquid two-phase refrigerant (point C) flows from the refrigerant inflow pipe 15 in the gas-liquid separator 5 as the gas-liquid two-phase refrigerant 19 in FIG.
  • the gas-liquid two-phase refrigerant 19 that has flowed in from the refrigerant inflow pipe 15 flows out from the front end of the outflow side end portion 15 a bent toward the inner wall of the first vertical pipe 11, and reaches the wall surface of the first vertical pipe 11. collide.
  • the gas-liquid two-phase refrigerant 19 is separated into gas and liquid by the liquid refrigerant 21 a having a large inertia adhering to the first vertical pipe 11.
  • the first vertical pipe 11 is not a container but a refrigerant pipe having a small cross-sectional area, foaming due to a collision hardly occurs.
  • coolant inflow piping 15 is bent so that it may orthogonally cross with respect to the inner wall of the 1st vertical piping 11, it is not limited to this.
  • the gas-liquid separation efficiency of the gas-liquid two-phase refrigerant 19 is improved.
  • the first vertical pipe 11 may be an internally grooved pipe. By doing so, there is an effect that foaming generated by the collision is suppressed by the surface tension of the groove.
  • the liquid refrigerant 21a separated from the gas-liquid two-phase refrigerant 19 receives gravity and proceeds downward as the liquid refrigerant 21b through the first vertical pipe 11 and the lower pipe 14. Thereafter, the liquid refrigerant 21 b accumulates in the lower part of the first vertical pipe 11, the lower pipe 14, and the lower part of the second vertical pipe 12, and flows out of the gas-liquid separator 5 from the liquid refrigerant outflow pipe 17.
  • the gas refrigerant 20a separated from the gas-liquid two-phase refrigerant 19 travels upward through the first vertical pipe 11 by the liquid refrigerant 21b accumulating in the lower part of the first vertical pipe 11, passes through the upper pipe 13, Further, the gas refrigerant 20c, which will be described later, has risen in the second vertical pipe 12, merges into the gas refrigerant 20d, and flows out of the gas-liquid separator 5 from the gas refrigerant outflow pipe 16.
  • the gas refrigerant 20b that is a part of the separated gas refrigerant 20a may be entrained.
  • the entrained gas refrigerant 20b flows into the second vertical pipe 12 via the lower pipe 14, receives buoyancy in the second vertical pipe 12, and then receives the liquid refrigerant 21b in the second vertical pipe 12.
  • the gas refrigerant 20a is separated from the liquid surface and proceeds upward through the second vertical pipe 12 as the gas refrigerant 20c, and merges with the gas refrigerant 20a flowing through the upper pipe 13 to form the gas refrigerant 20d from the gas refrigerant outflow pipe 16. It flows out of the gas-liquid separator 5.
  • the liquid refrigerant 21c which is a part of the liquid refrigerant 21a generated by the collision, pulls up the gas refrigerant 20a. 11 will rise.
  • the liquid refrigerant 21c is in the form of droplets or a liquid film along the inner wall of the tube.
  • the gas refrigerant outflow pipe 16 does not flow out from the gas-liquid separator 5 together with the gas refrigerant 20d.
  • the density of the liquid refrigerant 21c is larger than that of the gas refrigerant 20a flowing through the upper pipe 13, so that the liquid refrigerant 21c passes through the bottom of the upper pipe 13.
  • the second vertical pipe 12 is gravity dropped as the liquid refrigerant 21d and flows out from the liquid refrigerant outflow pipe 17.
  • the liquid refrigerant 21d needs to fall against the gas refrigerant 20c that rises in the second vertical pipe 12, but the gas refrigerant 20c that rises in the second vertical pipe 12 and the first vertical pipe 11 rise.
  • the gas refrigerant 20a that rises in the first vertical pipe 11 has a larger refrigerant amount, a higher flow rate, and the speed of the gas refrigerant 20c that rises in the second vertical pipe 12 is as follows. Since it is sufficiently slow, the liquid refrigerant 21d gravity falls through the second vertical pipe 12. On the other hand, when the liquid refrigerant 21c in the form of droplets is accompanied by the gas refrigerant 20a and reaches the second vertical pipe 12, the droplet adheres to the inner wall of the second vertical pipe 12 and becomes the second vertical pipe as the liquid refrigerant 21d. 12 falls by gravity and flows out from the liquid refrigerant outflow pipe 17.
  • the gas-liquid separator 5 acts as described above in the refrigeration cycle apparatus, and separates the gas-liquid two-phase refrigerant into the gas refrigerant and the liquid refrigerant with high gas-liquid separation efficiency. Can do.
  • the liquid refrigerant 21b (point E) that has flowed out of the gas-liquid separator 5 from the liquid refrigerant outflow pipe 17 flows into the second heat exchanger 6.
  • the liquid refrigerant that has flowed into the second heat exchanger 6 undergoes heat exchange with the room air, evaporates, becomes a gaseous refrigerant, and flows out of the second heat exchanger 6.
  • the gas refrigerant 20d (point F) flowing out from the gas refrigerant outflow pipe 16 to the outside of the gas-liquid separator 5 passes through the electromagnetic valve 7, the check valve 8 and the capillary tube 9 in the bypass circuit 10,
  • the gas refrigerant that has passed through the heat exchanger 6 joins (point D) flows into the compressor 1 via the four-way valve 2, and is compressed again.
  • the gas refrigerant 20d flowing out of the gas-liquid separator 5 from the gas refrigerant outflow pipe 16 may be returned to the suction side of the compressor 1, so that the bypass circuit 10 is connected to the compressor 1 as shown in FIG. It may be connected between the four-way valves 2.
  • the refrigeration cycle apparatus closes the electromagnetic valve 7 so that the refrigerant does not flow through the bypass circuit 10.
  • the high-temperature and high-pressure gaseous refrigerant compressed and discharged by the compressor 1 flows into the second heat exchanger 6 via the four-way valve 2.
  • the gaseous refrigerant that has flowed into the second heat exchanger 6 is subjected to heat exchange with the indoor air, is condensed, becomes liquid refrigerant, and flows out of the second heat exchanger 6.
  • the liquid refrigerant flowing out from the second heat exchanger 6 flows into the gas-liquid separator 5 from the liquid refrigerant outflow pipe 17.
  • the liquid refrigerant that has flowed into the gas-liquid separator 5 flows out of the refrigerant inflow pipe 15 in a liquid state.
  • the liquid refrigerant that has flowed out of the gas-liquid separator 5 flows into the expansion valve 4 and is expanded and depressurized by the expansion valve 4 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant.
  • This gas-liquid two-phase refrigerant flows into the first heat exchanger 3.
  • the gas-liquid two-phase refrigerant that has flowed into the first heat exchanger 3 undergoes heat exchange with the outside air, evaporates, becomes a gaseous refrigerant, and flows out of the first heat exchanger 3.
  • the gaseous refrigerant that has flowed out of the first heat exchanger 3 flows into the compressor 1 via the four-way valve 2 and is compressed again.
  • the present embodiment shown in FIG. 1 is performed except that the gas-liquid separator 5 does not pass.
  • the operation is the same as that of the refrigeration cycle apparatus equipped with the gas-liquid separator 5 according to the first embodiment.
  • the gas-liquid separator 5 can separate the gas-liquid two-phase refrigerant with high gas-liquid separation efficiency during the operation of the refrigeration cycle apparatus. Since the liquid separator 5 is composed only of the refrigerant pipe having no container, the manufacturing cost can be greatly reduced, the amount of refrigerant enclosed in the gas-liquid separator 5 can be reduced, and further the gas-liquid separation The device 5 can be reduced in size and thickness. Moreover, this makes it possible to reduce the size of the entire refrigeration cycle apparatus in which the gas-liquid separator 5 is mounted.
  • the second heat exchanger 6 allows only the liquid refrigerant to pass through the second heat exchanger 6.
  • the pressure loss when passing 6 can be reduced. For this reason, the required work amount at the time of compression in the compressor 1 can be reduced, and the coefficient of performance indicated by the ratio between the evaporation capability of the second heat exchanger 6 and the input of the compressor 1 can be improved. .
  • the gas-liquid separator 5 when the heating operation is performed, the gas-liquid separator 5 is configured by a refrigerant pipe that does not have a large container.
  • the liquid refrigerant that accumulates in the gas-liquid separator 5 can be greatly reduced, and the cost can be reduced accordingly.
  • the amount of refrigerant when a refrigerant with a large global warming potential is used, the amount of refrigerant can be greatly reduced, so the above effect is great.
  • the amount of flammable refrigerant such as hydrocarbon refrigerant can be greatly reduced.
  • the gas-liquid separator shown in FIG. 4 of Patent Document 1 described above is mounted on the refrigeration cycle apparatus (FIG. 1) according to the first embodiment and the heating operation is performed, liquid refrigerant is contained in the entire container. Since it accumulates, a large amount of refrigerant is required and the cost is greatly increased.
  • the bridge circuit shown in FIG. 3 of the same document is provided, and even when the operation is switched between the cooling operation and the heating operation, the gas-liquid separator It is necessary to make the inflow direction of the refrigerant flowing into the separator the same, resulting in an increase in cost due to the addition of a bridge circuit and an increase in the size of the entire apparatus.
  • the refrigeration cycle apparatus equipped with the gas-liquid separator 5 according to Embodiment 1 does not require a bridge circuit, and simplifies the configuration of the refrigeration cycle apparatus, reduces costs, and reduces the amount of refrigerant. be able to.
  • the refrigeration cycle apparatus equipped with the gas-liquid separator 5 according to Embodiment 1 does not require a bridge circuit, and simplifies the configuration of the refrigeration cycle apparatus, reduces costs, and reduces the amount of refrigerant. be able to.
  • the refrigeration cycle apparatus according to the first embodiment may of course be provided with a bridge circuit as shown in FIG. That is, in the refrigeration cycle apparatus according to the first embodiment, the refrigerant may flow into the gas-liquid separator 5 via the refrigerant inflow pipe 15 in both the cooling operation and the heating operation.
  • FIG. 5 is a configuration diagram showing another example of the refrigeration cycle apparatus equipped with the gas-liquid separator 5 according to Embodiment 1 of the present invention.
  • the refrigeration cycle apparatus shown in FIG. 5 includes a bridge circuit including four check valves (a first check valve 31a, a second check valve 31b, a third check valve 31c, and a fourth check valve 31d). 31 is provided. More specifically, the first check valve 31 a is installed between the liquid refrigerant outflow pipe 17 of the gas-liquid separator 5 and the first heat exchanger 3, and the refrigerant flows from the first heat exchanger 3. The flow is prevented from flowing in the direction toward the liquid refrigerant outflow pipe 17.
  • the second check valve 31b is installed between the liquid refrigerant outflow pipe 17 of the gas-liquid separator 5 and the second heat exchanger 6, and the refrigerant flows from the second heat exchanger 6 into the liquid refrigerant outflow pipe. 17 so that it does not flow in the direction to 17.
  • the third check valve 31c is installed between the first heat exchanger 3 and the expansion valve 4, and prevents refrigerant from flowing in the direction from the expansion valve 4 to the first heat exchanger 3. Is.
  • the fourth check valve 31d is installed between the second heat exchanger 6 and the expansion valve 4, and prevents refrigerant from flowing in the direction from the expansion valve 4 to the second heat exchanger 6. Further, in the refrigeration cycle apparatus shown in FIG.
  • the bypass circuit 10 has one end gas-liquid separated so that the bypass circuit 10 is connected to the suction side of the compressor 1 in both the cooling operation and the heating operation.
  • the other end is connected to a refrigerant pipe between the four-way valve 2 and the suction side of the compressor 1.
  • the refrigeration cycle apparatus when the refrigeration cycle apparatus performs the cooling operation, the refrigerant passes through the second heat exchanger 6 that operates as an evaporator.
  • the pressure loss at the time of carrying out can be reduced, and the coefficient of performance shown by the ratio of the evaporation capacity of the second heat exchanger 6 and the input of the compressor 1 can be improved.
  • the pressure loss when the refrigerant passes through the first heat exchanger 3 that operates as an evaporator can be reduced, and the evaporation of the first heat exchanger 3 can be reduced.
  • the coefficient of performance indicated by the ratio between the capacity and the input of the compressor 1 can be improved.
  • the manufacturing cost and the manufacturing efficiency can be improved.
  • the upper pipe 13, the first vertical pipe 11, and the lower pipe 14 are formed as an integral refrigerant pipe
  • the gas refrigerant outflow pipe 16, the second vertical pipe 12, and the liquid refrigerant outflow pipe 17 are formed as an integral refrigerant pipe.
  • the loop-shaped pipe 30 is formed by joining both refrigerant pipes, and the refrigerant inflow pipe 15 is inserted and joined to the first vertical pipe 11.
  • the refrigerant circulating through the refrigeration cycle apparatus according to Embodiment 1 is not particularly limited.
  • a fluorocarbon refrigerant such as R410A, R32, or R161
  • carbon dioxide or hydrocarbon which is a natural refrigerant
  • the refrigeration cycle apparatus can reduce the amount of refrigerant to be charged, even if it is used as a refrigerant having combustible hydrocarbons or tetrafluoropropene as a component, the refrigerant The amount of leakage at the time of leakage can be suppressed.
  • the gas-liquid separator 5 may be used in a circuit using the internal heat exchanger 60.
  • a part of the refrigerant condensed in the first heat exchanger 3 is branched to the internal heat exchanger bypass circuit 62.
  • the low-temperature refrigerant expanded and depressurized by the internal heat exchanger expansion valve 61 is subjected to heat exchange with the refrigerant flowing into the expansion valve 4 by the internal heat exchanger 60.
  • the refrigerant flowing into the expansion valve 4 is supercooled, and the dryness of the refrigerant expanded and depressurized by the expansion valve 4 becomes smaller.
  • the degree of dryness becomes small, the flow rate of the gas-liquid two-phase refrigerant flowing into the gas-liquid separator 5 becomes slower, the foaming in the first vertical pipe 11 is further suppressed, and the gas-liquid separation efficiency is increased. There is.
  • the flow rate becomes slow, when the flow rate is constant, the pipe diameter of the gas-liquid separator 5 can be made smaller, and the cost can be reduced.
  • the gas-liquid separation efficiency is increased, the dryness of the gas-liquid two-phase refrigerant flowing into the second heat exchanger 6 is reduced, and the dryness is close to 0, resulting in a substantially liquid single-phase flow.
  • the refrigerant distribution to the heat transfer tubes constituting the second heat exchanger 6 is improved when the single-phase flow is formed.
  • the performance of the second heat exchanger 6 serving as an evaporator can be improved.
  • a part of the refrigerant before entering the internal heat exchanger 60 is branched and supplied to the expansion valve 61 for the internal heat exchanger, but a part of the refrigerant after passing through the internal heat exchanger 60 is supplied.
  • the gas-liquid separator 5 may be used in a circuit using the internal heat exchanger 60 as shown in FIG. In FIG. 7, in the heating operation, a part of the refrigerant condensed in the second heat exchanger 6 is branched to the internal heat exchanger bypass circuit 62.
  • the low-temperature refrigerant expanded and depressurized by the internal heat exchanger expansion valve 61 is subjected to heat exchange with the refrigerant flowing into the expansion valve 4 by the internal heat exchanger 60. As a result, the refrigerant flowing into the expansion valve 4 is supercooled, and the dryness of the refrigerant expanded and depressurized by the expansion valve 4 becomes smaller.
  • the dryness becomes small, the flow rate of the gas-liquid two-phase refrigerant flowing into the gas-liquid separator 5 becomes slower, and the foaming in the first vertical pipe 11 is further suppressed, and the gas-liquid separation efficiency is increased. There is.
  • the flow rate is slow, when the flow rate is constant, the pipe diameter of the gas-liquid separator 5 can be made smaller, so there is a cost reduction effect.
  • the gas-liquid separation efficiency is increased, the dryness of the gas-liquid two-phase refrigerant flowing into the first heat exchanger 3 is reduced, the dryness is close to 0, and the liquid is substantially in a single-phase flow.
  • the refrigerant distribution to the heat transfer tubes constituting the first heat exchanger 3 becomes good when the single-phase flow is formed, and in FIG. 7, the performance of the first heat exchanger 3 serving as an evaporator can be improved.
  • a part of the refrigerant before entering the internal heat exchanger 60 is branched and supplied to the internal heat exchanger expansion valve 61.
  • a part of the refrigerant after passing through the internal heat exchanger 60 is supplied. You may branch and supply to the expansion valve 61 for internal heat exchangers. In the latter, the refrigerant before branching flowing through the internal heat exchanger and the refrigerant after branching are in opposite flows.
  • the gas-liquid two-phase refrigerant flowing out of the expansion valve 4 is gas-liquid separated by the gas-liquid separator 5 only during the cooling operation.
  • the present invention is not limited to this.
  • the connection order of the expansion valve 4 and the gas-liquid separator 5 is reversed, and the bypass circuit 10 is connected to the refrigerant pipe connecting the first heat exchanger 3 and the four-way valve 2.
  • the gas-liquid two-phase refrigerant that has flowed out of the expansion valve 4 by the gas-liquid separator 5 may be gas-liquid separated. Even in this case, the same effect as described above can be obtained.
  • bypass circuit 10 if the bypass circuit 10 is connected between the four-way valve 2 and the suction side of the compressor 1, the gas-liquid two-phase refrigerant is separated into gas and liquid only during the cooling operation, and only during the heating operation.
  • gas-liquid separation of the gas-liquid two-phase refrigerant it is not necessary to switch the connection destination of the bypass circuit 10 as described above.
  • the bypass circuit 10 connecting the gas-liquid separator 5 to the suction side of the compressor 1 includes the electromagnetic valve 7, the check valve 8, and the capillary tube 9, but is not limited thereto. It is good also as a structure provided with a flow regulating valve instead of these.
  • the refrigerant inflow pipe 15 is inserted into the first vertical pipe 11 from the junction of the upper pipe 13 and the first vertical pipe 11, but the insertion position and the insertion direction of the refrigerant inflow pipe 15 are included. Is optional.
  • the refrigerant inflow pipe 15 may be inserted into the first vertical pipe 11 from the junction of the lower pipe 14 and the first vertical pipe 11, or the refrigerant inflow pipe 15 may be inserted into the first vertical pipe 11 from the side surface. It may be inserted into the vertical pipe 11.
  • the upper pipe 13 is located outside the loop pipe 30 between the upper end portion of the first vertical pipe 11 and the upper end portion of the second vertical pipe 12 positioned above the upper end portion of the first vertical pipe 11.
  • the present invention is not limited to this.
  • the lower pipe 14 is located outside the loop pipe 30 between the lower end of the first vertical pipe 11 and the lower end of the second vertical pipe 12 positioned below the lower end of the first vertical pipe 11.
  • the present invention is not limited to this.
  • the upper pipe 13 may be formed so that the joining portion of the upper pipe 13 and the first vertical pipe 11 has a right-angle shape instead of an arc shape.
  • the refrigerant inflow pipe 15 is inserted into the first vertical pipe 11 from the joining part of the lower pipe 14 and the first vertical pipe 11, the joining part of the lower pipe 14 and the first vertical pipe 11 has a right-angle shape.
  • the lower pipe 14 may be formed. The insertion and joining of the refrigerant inflow pipe 15 into the first vertical pipe 11 is facilitated, and the cost can be reduced.
  • the gas-liquid separator 5 including the first vertical pipe 11 and the second vertical pipe 12 is arranged so as to be in a substantially vertical direction, but is not limited thereto.
  • the plane formed by the loop-shaped pipe 30 may be arranged at a predetermined angle from the horizontal plane so that the plane does not change from the vertical direction to the horizontal direction. Even with such an arrangement, the same effects as described above can be obtained, and the degree of freedom of the arrangement of the gas-liquid separator 5 in the refrigeration cycle apparatus can be improved.
  • the cross-sectional area of each flow path of the gas-liquid separator 5 is not particularly limited.
  • the gas-liquid separator 5 is constituted by the refrigerant pipes having the same diameter, the types of the refrigerant pipes can be unified, so that parts management is facilitated.
  • the air conditioner has been described as an example of the refrigeration cycle apparatus according to the first embodiment, but the present invention is not limited to this, and is applied to other refrigeration cycle apparatuses such as a heat pump hot water supply apparatus or a refrigerator. It is good.
  • the gas-liquid separator 5 according to the first embodiment is mounted on the refrigeration cycle apparatus, but is not limited to this, and is applied to the gas-liquid separation of other fluids instead of the refrigerant. It is good.
  • Embodiment 2 FIG. The gas-liquid separator 5 according to the second embodiment will be described focusing on differences from the configuration and operation of the gas-liquid separator 5 according to the first embodiment.
  • the configuration of the refrigeration cycle apparatus according to Embodiment 2 is the same as the configuration of the refrigeration cycle apparatus according to Embodiment 1 shown in FIG.
  • FIG. 9 is a configuration diagram of the gas-liquid separator 5 according to Embodiment 2 of the present invention.
  • the gas-liquid separator 5 according to the second embodiment is arranged in a substantially vertical direction, as well as a first vertical pipe 11 as a first refrigerant channel arranged in a substantially vertical direction.
  • the second vertical pipe 12 as the second refrigerant flow path
  • the upper pipe 13 as a connecting portion connecting the upper end of the first vertical pipe 11 and the upper end of the second vertical pipe 12
  • the first vertical pipe A lower pipe 14 is provided as a connecting part that connects the lower end of the pipe 11 and the lower end of the second vertical pipe 12.
  • the first vertical pipe 11, the second vertical pipe 12, the upper pipe 13 and the lower pipe 14 form a loop pipe 30.
  • the gas-liquid separator 5 includes a refrigerant inflow pipe 15 in which an outflow side end portion 15 a is inserted into the first vertical pipe 11 as a refrigerant inflow path into the first vertical pipe 11.
  • An outflow portion 50 through which the gas-liquid two-phase refrigerant flowing into the refrigerant inflow piping 15 flows out is formed at the outflow side end portion 15a of the refrigerant inflow piping 15.
  • the opening at the front end portion of the outflow side end portion 15a is used as the outflow portion 50 as it is.
  • the refrigerant inflow piping 15 which concerns on this Embodiment 2 is bent so that the outflow side edge part 15a may face the inner wall of the 1st vertical piping 11. As shown in FIG.
  • the upper pipe 13 is a refrigerant pipe that joins the gas refrigerant 20a rising in the first vertical pipe 11 with the gas refrigerant 20c rising in the second vertical pipe 12, as will be described later. Further, the upper pipe 13 is located outside the loop pipe 30 between the upper end portion of the first vertical pipe 11 and the upper end portion of the second vertical pipe 12 positioned above the upper end portion of the first vertical pipe 11. It forms so that it may become circular arc shape toward.
  • the lower pipe 14 is a refrigerant pipe that sends the liquid refrigerant 21b descending in the first vertical pipe 11 to the lower end of the second vertical pipe 12, as will be described later. Further, the lower pipe 14 is located outside the loop pipe 30 between the lower end of the first vertical pipe 11 and the lower end of the second vertical pipe 12 positioned below the lower end of the first vertical pipe 11. It forms so that it may become circular arc shape toward.
  • the tip of the outflow side end 15a of the refrigerant inflow pipe 15 is inserted between the uppermost point and the lowermost point of the loop-shaped pipe 30 at a position having a ratio of H1: H2 in the vertical direction.
  • the distance H1 only needs to be sufficiently high in the gas-liquid separation of the gas-liquid two-phase refrigerant, and the ratio of H1: H2 is not limited, but is about 2: 1 to 3: 1, for example. You only have to set it.
  • the lower pipe 14 and the loop-shaped pipe 30 correspond to the “first lower pipe” and the “first loop-shaped pipe” in the present invention, respectively.
  • the gas-liquid separator 5 further includes a third vertical pipe 120 serving as a third refrigerant channel arranged in a substantially vertical direction, an upper end portion of the second vertical pipe 12, and a third vertical pipe.
  • An upper pipe 130 serving as a connecting part that connects the upper end part of 120 and a lower pipe 140 serving as a connecting part that connects the lower end part of the second vertical pipe 12 and the lower end part of the third vertical pipe 120 are provided.
  • the gas-liquid separator 5 includes a gas refrigerant outflow pipe 160 connected to an upper pipe 130 (more specifically, a junction between the third vertical pipe 120 and the upper pipe 130), and a lower pipe 140 (more specifically, A liquid refrigerant outflow pipe 170 connected to the third vertical pipe 120 and the lower pipe 140 is provided.
  • the gas refrigerant outlet pipe 160 extends upward from the upper pipe 130, and the liquid refrigerant outlet pipe 170 extends downward from the lower pipe 140.
  • the second vertical pipe 12, the third vertical pipe 120, the upper pipe 130 and the lower pipe 140 form a loop pipe 300.
  • the upper pipe 130 includes a gas refrigerant 20a that rises in the first vertical pipe 11 and the upper pipe 13 and a gas refrigerant 20c that rises in the second vertical pipe 12 in the third vertical pipe 120. Is a refrigerant pipe that merges with the rising gas refrigerant 20f.
  • the lower pipe 140 is a refrigerant pipe that sends the liquid refrigerant 21e descending in the second vertical pipe 12 to the third vertical pipe 120 and the liquid refrigerant outflow pipe 170, as will be described later.
  • the lower pipe 140 is disposed between the lower end of the second vertical pipe 12 and the lower end of the third vertical pipe 120 positioned below the lower end of the second vertical pipe 12. It forms so that it may become circular arc shape toward.
  • the lower pipe 14 described above is orthogonal to the second vertical pipe 12 at a position where the ratio of H1 ′: H2 ′ is vertically established between the uppermost point and the lowermost point of the loop-shaped pipe 300. It is connected. Further, the distance H1 ′ may be sufficiently high in the gas-liquid separation of the liquid refrigerant 21b and the gas refrigerant 20b involved in the distance, and the ratio of H1 ′: H2 ′ is not limited. It may be set to about 2: 1 to 4: 1.
  • the third vertical pipe 120, the lower pipe 140, and the loop-shaped pipe 300 correspond to “third pipe”, “second lower pipe”, and “second loop-shaped pipe” in the present invention, respectively.
  • the gas-liquid two-phase refrigerant that has flowed out of the expansion valve 4 flows from the refrigerant inflow pipe 15 in the gas-liquid separator 5 as the gas-liquid two-phase refrigerant 19 in FIG.
  • the gas-liquid two-phase refrigerant 19 flowing from the refrigerant inflow pipe 15 collides with the inner wall of the first vertical pipe 11. Due to this collision, the gas-liquid two-phase refrigerant 19 is separated into gas and liquid by the liquid refrigerant 21 a having a large inertia adhering to the first vertical pipe 11. At this time, since the first vertical pipe 11 is not a container but a refrigerant pipe having a small cross-sectional area, foaming due to a collision hardly occurs.
  • coolant inflow piping 15 is bent so that it may orthogonally cross with respect to the inner wall of the 1st vertical piping 11, it is not limited to this.
  • the gas-liquid separation efficiency of the gas-liquid two-phase refrigerant 19 is improved.
  • the liquid refrigerant 21a separated from the gas-liquid two-phase refrigerant 19 receives gravity, travels downward through the first vertical pipe 11 and the lower pipe 14 as the liquid refrigerant 21b, and flows into the second vertical pipe 12.
  • the gas refrigerant 20a separated from the gas-liquid two-phase refrigerant 19 travels upward through the first vertical pipe 11 by the liquid refrigerant 21b accumulating in the lower part of the first vertical pipe 11, passes through the upper pipe 13, A gas refrigerant 20c, which will be described later, has risen through the second vertical pipe 12, and merges at the upper end of the second vertical pipe 12, and further, a gas refrigerant 20f, which will be described later, has risen through the third vertical pipe 120 and the third vertical pipe 120. They merge at the upper end and become the gas refrigerant 20d and flow out of the gas-liquid separator 5 from the gas refrigerant outflow pipe 160.
  • the gas refrigerant 20b that is a part of the separated gas refrigerant 20a may be entrained. At this time, the entrained gas refrigerant 20b flows into the second vertical pipe 12 together with the liquid refrigerant 21b.
  • the liquid refrigerant 21b including the gas refrigerant 20b crosses the second vertical pipe 12 and collides with the wall surface of the second vertical pipe 12. Due to this collision, most of the gas refrigerant 20b entrained in the liquid refrigerant 21b rises due to buoyancy in the second vertical pipe 12, and the liquid refrigerant 21b receives gravity and becomes the second vertical refrigerant 21e. The pipe 12 and the lower pipe 140 are moved downward. Thereafter, the liquid refrigerant 21e accumulates in the lower part of the second vertical pipe 12, the lower pipe 140, and the lower part of the third vertical pipe 120, and flows out of the gas-liquid separator 5 from the liquid refrigerant outflow pipe 170.
  • the gas refrigerant 20b separated from the liquid refrigerant 21b including the gas refrigerant 20b receives buoyancy in the second vertical pipe 12 as described above, and the liquid refrigerant 21b in the second vertical pipe 12
  • the gas refrigerant 20c proceeds upward through the second vertical pipe 12, merges with the gas refrigerant 20a flowing through the upper pipe 13, and further rises up the third vertical pipe 120, which will be described later.
  • the gas refrigerant 20f joins at the upper end of the third vertical pipe 120 and becomes the gas refrigerant 20d and flows out of the gas-liquid separator 5 from the gas refrigerant outflow pipe 160.
  • a part of the gas refrigerant 20b in the liquid refrigerant 21b is entrained in the liquid refrigerant 21e as the gas refrigerant 20e, and the entrained gas refrigerant 20e flows into the third vertical pipe 120 via the lower pipe 140, Upon receiving buoyancy in the third vertical pipe 120, the liquid is separated from the liquid level of the liquid refrigerant 21e in the third vertical pipe 120, and proceeds upward through the third vertical pipe 120 as the gas refrigerant 20f.
  • the gas refrigerant 20a and the gas refrigerant 20c that have flowed through the gas further merge with the refrigerant, and the gas refrigerant 20d flows out of the gas-liquid separator 5 from the gas refrigerant outlet pipe 160.
  • the liquid refrigerant 21c which is a part of the liquid refrigerant 21a generated by the collision, pulls up the gas refrigerant 20a. 11 will rise.
  • the liquid refrigerant 21c is in the form of droplets or a liquid film along the inner wall of the tube.
  • the distance H1 from the end of the refrigerant inflow pipe 15 to the uppermost point of the loop-shaped pipe 30 is increased, the liquid film-like liquid refrigerant 21c falls by gravity, so that the gas refrigerant 20d is discharged from the gas refrigerant outflow pipe 160.
  • the gas-liquid separator 5 does not flow out.
  • the density of the liquid refrigerant 21c is larger than that of the gas refrigerant 20a flowing through the upper pipe 13, so that the liquid refrigerant 21c passes through the bottom of the upper pipe 13.
  • the second vertical pipe 12 is gravity dropped as the liquid refrigerant 21d and flows out from the liquid refrigerant outflow pipe 170 as a part of the liquid refrigerant 21e.
  • the liquid refrigerant 21d needs to fall against the gas refrigerant 20c that rises in the second vertical pipe 12, but the gas refrigerant 20c that rises in the second vertical pipe 12 and the first vertical pipe 11 rise.
  • the gas refrigerant 20a that rises in the first vertical pipe 11 has a larger refrigerant amount, a higher flow rate, and the speed of the gas refrigerant 20c that rises in the second vertical pipe 12 is as follows. Since it is sufficiently slow, the liquid refrigerant 21d gravity falls through the second vertical pipe 12.
  • the liquid refrigerant 21c reaches the upper pipe 13 and further does not drop in the second vertical pipe 12 by gravity and reaches the upper pipe 130, the density of the liquid refrigerant 21c flows through the upper pipe 130. Since the liquid refrigerant 21c flows through the bottom of the upper pipe 130 and reaches the third vertical pipe 120, the liquid refrigerant 21c is gravity as the liquid refrigerant 21f. It falls and becomes part of the liquid refrigerant 21e and flows out from the liquid refrigerant outflow pipe 170.
  • the liquid refrigerant 21f needs to fall against the gas refrigerant 20f rising in the third vertical pipe 120, but the gas refrigerant 20f rising in the third vertical pipe 120 and the gas refrigerant flowing through the upper pipe 130 Comparing the refrigerant combined with 20a and the gas refrigerant 20c, the refrigerant combined with the gas refrigerant 20a and the gas refrigerant 20c flowing through the upper pipe 130 has a larger refrigerant amount, a higher flow rate, and the third Since the speed of the gas refrigerant 20f rising up the vertical pipe 120 is sufficiently low, the liquid refrigerant 21f gravity falls through the third vertical pipe 120.
  • liquid refrigerant 21c in the form of droplets is accompanied by the gas refrigerant 20a and the gas refrigerant 20c and reaches the third vertical pipe 120
  • the liquid droplets adhere to the inner wall of the third vertical pipe 120 and become the liquid refrigerant 21f. It falls in the third vertical pipe 120 by gravity and flows out from the liquid refrigerant outflow pipe 170.
  • the gas-liquid separator 5 according to the second embodiment operates as described above in the refrigeration cycle apparatus, and makes the collision part multistage, thereby making the gas-liquid separator 5 according to the first embodiment more Further, the gas-liquid two-phase refrigerant can be separated into the gas refrigerant and the liquid refrigerant with high gas-liquid separation efficiency.
  • the gas-liquid separator 5 according to the second embodiment has a gas-liquid two-phase operation with higher gas-liquid separation efficiency than the gas-liquid separator 5 according to the first embodiment when the refrigeration cycle apparatus is operated.
  • the refrigerant in the state can be separated, and the gas-liquid separator 5 is composed only of the refrigerant pipe having no container, so that the manufacturing cost can be greatly reduced, and the amount of refrigerant to be enclosed is reduced.
  • the gas-liquid separator 5 can be reduced in size and thickness. Moreover, this makes it possible to reduce the size of the entire refrigeration cycle apparatus in which the gas-liquid separator 5 is mounted.
  • Embodiment 3 FIG.
  • the gas-liquid separator 5 according to the third embodiment will be described focusing on differences from the configuration and operation of the gas-liquid separator 5 according to the first embodiment.
  • the configuration of the refrigeration cycle apparatus according to Embodiment 3 is the same as that of the refrigeration cycle apparatus according to Embodiment 1 shown in FIG.
  • FIG. 10 is a structural diagram of the gas-liquid separator 5 according to Embodiment 3 of the present invention.
  • the gas-liquid separator 5 according to the present embodiment obliquely disposes the outlet side end portion 15 a of the refrigerant inlet pipe 15 in the gas-liquid separator 5 according to Embodiment 1 shown in FIG. 2. It is cut into pieces. And the opening of this front-end
  • Embodiment 4 FIG.
  • the gas-liquid separator 5 according to the fourth embodiment will be described focusing on differences from the configuration and operation of the gas-liquid separator 5 according to the first embodiment.
  • the configuration of the refrigeration cycle apparatus according to Embodiment 4 is the same as the configuration of the refrigeration cycle apparatus according to Embodiment 1 shown in FIG.
  • FIG. 12 is a structural diagram of the gas-liquid separator 5 according to Embodiment 4 of the present invention.
  • the gas-liquid separator 5 according to the fourth embodiment seals the opening at the front end of the outflow side end 15a of the refrigerant inflow pipe 15 according to the first embodiment shown in FIG.
  • a plurality of through holes 51 are provided in the side surface portion of the outflow side end portion 15 a as the outflow portion 50 so as to face the inner wall of the first vertical pipe 11.
  • the gas-liquid two-phase refrigerant 19 can collide with the wall surface of the first vertical pipe 11 without bending the outflow side end portion 15a.
  • coolant 19 which collides with the inner wall of the 1st vertical piping 11 can be lowered
  • the gas-liquid two-phase refrigerant can be separated into the gas refrigerant and the liquid refrigerant with higher gas-liquid separation efficiency.
  • the apparent gas velocity of the gas-liquid two-phase refrigerant 19 ejected from the through hole 51 is 2.0 m / sec or less, preferably 1.6 m / sec or less, based on the evaluation result of the gas-liquid separation efficiency by experiment. It was found that the gas-liquid separation efficiency was further improved by setting the diameter and number of the through-holes 51 to each other.
  • FIG. The gas-liquid separator 5 according to the fifth embodiment will be described focusing on differences from the configuration and operation of the gas-liquid separator 5 according to the first embodiment.
  • the configuration of the refrigeration cycle apparatus according to the present embodiment is the same as the configuration of the refrigeration cycle apparatus according to Embodiment 1 shown in FIG.
  • FIG. 14 is a configuration diagram of the gas-liquid separator 5 according to Embodiment 5 of the present invention.
  • the gas-liquid separator 5 according to the fifth embodiment is the same as the gas-liquid separator 5 according to the first embodiment shown in FIG.
  • the internal diameter of the surrounding 1st vertical piping 11 is enlarged.
  • the speed at which the liquid refrigerant 21a colliding with and adhering to the inner wall of the first vertical pipe 11 descends on the wall surface by gravity is reduced, and the liquid level disturbance of the liquid refrigerant 21b accumulated below the first vertical pipe 11 is suppressed.
  • the inner diameter of the first vertical pipe 11 is increased, the rising speed of the gas refrigerant 20a rising in the first vertical pipe 11 is slowed, and the amount of the liquid refrigerant 21c in the form of droplets accompanying the gas refrigerant 20a is reduced. Can be suppressed.
  • coolant inflow piping 15 are arbitrary.
  • the refrigerant inflow pipe 15 may be inserted from the side surface portion of the first vertical pipe 11. By doing so, it is easier to process than inserting the refrigerant inflow pipe 15 into the arc-shaped upper pipe 13, and the processing cost is reduced. Further, as shown in FIG. 16, if the refrigerant inflow pipe 15 is inserted substantially vertically into the side surface portion of the first vertical pipe 11, the processing becomes easier and the processing cost is reduced.
  • Embodiment 6 FIG.
  • the gas-liquid separator 5 according to the sixth embodiment will be described focusing on differences from the configuration and operation of the gas-liquid separator 5 according to the first embodiment.
  • the configuration of the refrigeration cycle apparatus according to Embodiment 6 is the same as the configuration of the refrigeration cycle apparatus according to Embodiment 1 shown in FIG.
  • FIG. 17 is a structural diagram of the gas-liquid separator 5 according to Embodiment 6 of the present invention.
  • the gas-liquid separator 5 according to the sixth embodiment has a mesh 40 provided below the first vertical pipe 11 in the gas-liquid separator 5 (FIG. 2) according to the first embodiment. It is provided.
  • the mesh 40 is disposed below the outflow portion 50 of the refrigerant inflow pipe 15.
  • Embodiment 7 FIG.
  • the gas-liquid separator 5 according to the seventh embodiment will be described focusing on differences from the configuration and operation of the gas-liquid separator 5 according to the first embodiment.
  • the configuration of the refrigeration cycle apparatus according to Embodiment 7 is the same as the configuration of the refrigeration cycle apparatus according to Embodiment 1 shown in FIG.
  • FIG. 18 is a structural diagram of the gas-liquid separator 5 according to Embodiment 7 of the present invention.
  • the gas-liquid separator 5 according to the seventh embodiment includes a mesh 40 above the first vertical pipe 11 in the gas-liquid separator 5 (FIG. 2) according to the first embodiment. It is a thing.
  • the mesh 40 is disposed above the outflow part 50 of the refrigerant inflow pipe 15.
  • Embodiment 8 FIG.
  • the gas-liquid separator 5 according to the eighth embodiment will be described focusing on differences from the configuration and operation of the gas-liquid separator 5 according to the first embodiment.
  • the configuration of the refrigeration cycle apparatus according to Embodiment 8 is the same as the configuration of the refrigeration cycle apparatus according to Embodiment 1 shown in FIG.
  • FIG. 19 is a structural diagram of the gas-liquid separator 5 according to the eighth embodiment of the present invention.
  • the gas-liquid separator 5 according to the present embodiment includes a mesh 40 on the inner wall of the first vertical pipe 11 in the gas-liquid separator 5 (FIG. 2) according to the first embodiment. Is.
  • the mesh 40 is installed at least on the inner wall of the first vertical pipe 11 in a range where the gas-liquid two-phase refrigerant 19 flowing out from the outflow portion 50 of the refrigerant inflow pipe 15 collides.
  • the mesh specification is preferably about 0.1 mm in wire diameter and mesh # 100 (100 lines are arranged in 1 inch).
  • Embodiment 9 FIG.
  • the gas-liquid separator 5 according to the ninth embodiment will be described focusing on differences from the configuration and operation of the gas-liquid separator 5 according to the first embodiment.
  • the configuration of the refrigeration cycle apparatus according to Embodiment 9 is the same as the configuration of the refrigeration cycle apparatus according to Embodiment 1 shown in FIG.
  • FIG. 20 is a structural diagram of the gas-liquid separator 5 according to the ninth embodiment of the present invention.
  • the gas-liquid separator 5 according to the ninth embodiment has a first vertical pipe instead of the second vertical pipe 12 in the gas-liquid separator 5 (FIG. 2) according to the first embodiment.
  • a second vertical pipe 12 a having a smaller diameter than the pipe 11 is provided.
  • the gas refrigerant 20c flows through the second vertical pipe 12a.
  • the second vertical pipe 12a corresponds to the “second pipe” in the present invention.
  • the gas-liquid separator 5 according to the second embodiment shown in FIG. 9 instead of the second vertical pipe 12 and the third vertical pipe 120, rather than the first vertical pipe 11.
  • the second vertical pipe 12a having a small diameter and the third vertical pipe 120a having a smaller diameter than the second vertical pipe 12a may be provided.
  • the gas-liquid separator 5 according to Embodiments 3 to 8 may have the same configuration. Even in these cases, the same effect as described above can be obtained.

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  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

La présente invention a trait à un séparateur de gaz-liquide (5) qui est équipé : d'une première canalisation verticale (11) ; d'une seconde canalisation verticale (12) ; d'une canalisation de partie supérieure (13) permettant de connecter une partie supérieure de la première canalisation verticale (11) à une partie supérieure de la seconde canalisation verticale (12) ; d'une canalisation de partie inférieure (14) permettant de connecter une partie inférieure de la première canalisation verticale (11) à une partie inférieure de la seconde canalisation verticale (12) ; d'une canalisation d'arrivée de fluide frigorigène (15) à partir de laquelle un fluide frigorigène biphasique gaz-liquide s'écoule dans la première canalisation verticale (11) ; d'une canalisation de sortie de fluide frigorigène gazeux (16) qui est connectée à la canalisation de partie supérieure (13), à partir de laquelle un fluide frigorigène en phase gazeuse s'écoule ; et d'une canalisation de sortie de fluide frigorigène liquide (17) qui est connectée à la canalisation de partie inférieure (14), à partir de laquelle un fluide frigorigène en phase liquide s'écoule. Une section de sortie (50) à partir de laquelle le fluide frigorigène biphasique gaz-liquide s'écoule est formée sur une extrémité côté sortie (15a) de la canalisation d'arrivée de fluide frigorigène (15). L'extrémité côté sortie (15a) est insérée dans la première canalisation verticale (11). La section de sortie (50) est formée de manière à ce que le fluide frigorigène biphasique gaz-liquide puisse entrer en collision avec la paroi intérieure de la première canalisation verticale (11), ledit fluide frigorigène biphasique gaz-liquide ayant circulé dans la première canalisation verticale (11).
PCT/JP2012/002497 2011-04-25 2012-04-11 Séparateur de gaz-liquide et appareil à cycle de réfrigération équipé du séparateur de gaz-liquide Ceased WO2012147290A1 (fr)

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JP2013511902A JP5634597B2 (ja) 2011-04-25 2012-04-11 気液分離器及びこの気液分離器を搭載した冷凍サイクル装置

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JP2011-096937 2011-04-25
JP2011096937 2011-04-25

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WO2012147290A1 true WO2012147290A1 (fr) 2012-11-01

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WO (1) WO2012147290A1 (fr)

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WO2015002086A1 (fr) * 2013-07-02 2015-01-08 三菱電機株式会社 Circuit de réfrigérant et dispositif de climatisation
JP2017526887A (ja) * 2014-08-18 2017-09-14 青島海爾洗衣机有限公司ＱｉｎｇＤａｏ Ｈａｉｅｒ Ｗａｓｈｉｎｇ Ｍａｃｈｉｎｅ Ｃｏ．，Ｌｔｄ． ヒートポンプシステム、洗濯乾燥機及び乾燥機
WO2019021431A1 (fr) * 2017-07-27 2019-01-31 三菱電機株式会社 Appareil à cycle frigorifique
JP2021042881A (ja) * 2019-09-09 2021-03-18 ホシザキ株式会社 冷却貯蔵庫

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WO2015002086A1 (fr) * 2013-07-02 2015-01-08 三菱電機株式会社 Circuit de réfrigérant et dispositif de climatisation
CN105358918A (zh) * 2013-07-02 2016-02-24 三菱电机株式会社 制冷剂回路和空调装置
JPWO2015002086A1 (ja) * 2013-07-02 2017-02-23 三菱電機株式会社 冷媒回路および空気調和装置
CN105358918B (zh) * 2013-07-02 2017-06-27 三菱电机株式会社 制冷剂回路和空调装置
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JP2017526887A (ja) * 2014-08-18 2017-09-14 青島海爾洗衣机有限公司ＱｉｎｇＤａｏ Ｈａｉｅｒ Ｗａｓｈｉｎｇ Ｍａｃｈｉｎｅ Ｃｏ．，Ｌｔｄ． ヒートポンプシステム、洗濯乾燥機及び乾燥機
WO2019021431A1 (fr) * 2017-07-27 2019-01-31 三菱電機株式会社 Appareil à cycle frigorifique
CN110892213A (zh) * 2017-07-27 2020-03-17 三菱电机株式会社 制冷循环装置
JPWO2019021431A1 (ja) * 2017-07-27 2020-03-19 三菱電機株式会社 冷凍サイクル装置
CN110892213B (zh) * 2017-07-27 2021-08-27 三菱电机株式会社 制冷循环装置
JP2021042881A (ja) * 2019-09-09 2021-03-18 ホシザキ株式会社 冷却貯蔵庫
JP7386018B2 (ja) 2019-09-09 2023-11-24 ホシザキ株式会社 冷却貯蔵庫

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