EP3009773A1 - Climatiseur - Google Patents

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Publication number
EP3009773A1
EP3009773A1 EP14810377.3A EP14810377A EP3009773A1 EP 3009773 A1 EP3009773 A1 EP 3009773A1 EP 14810377 A EP14810377 A EP 14810377A EP 3009773 A1 EP3009773 A1 EP 3009773A1
Authority
EP
European Patent Office
Prior art keywords
valve
needle
expansion valve
refrigerant
pressure
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.)
Granted
Application number
EP14810377.3A
Other languages
German (de)
English (en)
Other versions
EP3009773B1 (fr
EP3009773A4 (fr
Inventor
Masashi Saito
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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Publication date
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Publication of EP3009773A1 publication Critical patent/EP3009773A1/fr
Publication of EP3009773A4 publication Critical patent/EP3009773A4/fr
Application granted granted Critical
Publication of EP3009773B1 publication Critical patent/EP3009773B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B2400/16—Receivers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

Definitions

  • the present invention relates to an air conditioning apparatus, and particularly to an air conditioning apparatus having a refrigerant circuit configured by connecting a compressor, an outdoor heat exchanger, a first expansion valve, a receiver, an opening/closing valve, and an indoor heat exchanger.
  • the air conditioning apparatus has a refrigerant circuit configured by connecting a compressor, an outdoor heat exchanger, a first expansion valve, a receiver, a second expansion valve (an opening/closing valve), and an indoor heat exchanger.
  • liquid sealing means a state in which a predetermined space in the refrigerant circuit is filled with liquid refrigerant and the liquid refrigerant becomes sealed within the predetermined space, and problems occur such as the equipment constituting the predetermined space rupturing due to an increase in temperature.
  • the portion in the refrigerant circuit between the two expansion valves including the receiver is filled with liquid refrigerant, the liquid refrigerant becomes sealed in this portion, and there is a risk of problems such as an increase in temperature causing the receiver and other equipment constituting this portion to rupture.
  • Patent Literature 1 an injection pipe is provided for drawing refrigerant out of the upper space of the receiver and injecting the refrigerant into the compressor, and a fully-closing expansion valve could be used as a degassing valve provided to this injection pipe, but there is still a risk of liquid sealing in the receiver when the three expansion valves are fully closed in this case as well.
  • a fully-closing expansion valve e.g., a first expansion valve
  • a liquid-side shut-off valve is provided to the other of the upstream side and downstream side of the receiver
  • a liquid sealing prevention pipe must be provided to enable refrigerant to be let out at any time from the upper space of the receiver, but because providing such a liquid sealing prevention pipe increases cost and causes problems with installation space, it would be preferable to prevent liquid sealing in the receiver without providing a liquid sealing prevention pipe.
  • An object of the present invention is to provide an air conditioning apparatus having a refrigerant circuit configured by connecting a compressor, an outdoor heat exchanger, a first expansion valve, a receiver, an opening/closing valve, and an indoor heat exchanger, wherein liquid sealing in the receiver can be prevented using fully-closing expansion valves, without providing a liquid sealing prevention pipe.
  • An air conditioning apparatus is an air conditioning apparatus having a refrigerant circuit configured by connecting a compressor, an outdoor heat exchanger, a first expansion valve, a receiver, an opening/closing valve, and an indoor heat exchanger.
  • a fully-closing expansion valve that is fully closed by a needle sitting on a valve seat is used as the first expansion valve, and the first expansion valve is provided to the refrigerant circuit in a first disposed state in which refrigerant from the receiver flows in from a needle advancing direction side of the valve seat, and out to a needle retracting direction side of the valve seat through a gap between the needle and the valve seat, the needle advancing direction being the direction in which the needle moves when the needle sits on the valve seat, and the needle retracting direction being the direction in which the needle moves when the needle retracts from the valve seat.
  • the first expansion valve provided to the refrigerant circuit in the first disposed state has a spring for urging the needle seated on the valve seat in the needle advancing direction when the valve is fully closed, the first expansion valve being configured so that the needle is released from sitting on the valve seat when the urging force of the spring in the needle advancing direction is overcome by a force pushing the needle in the needle retracting direction as generated by a counter-pressure valve-opening pressure difference, which is the difference between refrigerant pressure in a space on the needle retracting direction side of the valve seat and refrigerant pressure in a space on the needle advancing direction side of the valve seat.
  • the refrigerant in the portion of the refrigerant circuit between the first expansion valve and the opening/closing valve including the receiver must be able to be let to the rest of the refrigerant circuit in order to make liquid sealing in the receiver preventable without providing a liquid sealing prevention pipe, even when the first expansion valve and the opening/closing valve are fully closed.
  • the first expansion valve herein is provided to the refrigerant circuit in a first disposed state in which refrigerant from the receiver flows in from the needle advancing direction side of the valve seat, through a gap between the needle and the valve seat, and out to the needle retracting direction side of the valve seat, as described above.
  • a force will thereby act to push the needle in the needle retracting direction when the counter-pressure valve-opening pressure difference occurs, which is the difference between refrigerant pressure in the space on the needle retracting direction side of the valve seat and refrigerant pressure in the space on the needle advancing direction side of the valve seat when the first expansion valve is fully closed.
  • the force pushing the needle in the needle retracting direction due to this counter-pressure valve-opening pressure difference is utilized to provide a configuration in which the first expansion valve provided to the refrigerant circuit in the first disposed state is provided with the spring for urging the needle seated on the valve seat in the needle advancing direction when the valve is fully closed, and when the force pushing the needle in the needle retracting direction due to the counter-pressure valve-opening pressure difference overcomes the urging force of the spring in the needle advancing direction, the needle is released from sitting on the valve seat.
  • liquid sealing in the receiver can be prevented without providing a liquid sealing prevention pipe, despite a fully-closing expansion valve being used as the first expansion valve.
  • the refrigerant circuit is configured with a fully-closing first expansion valve provided to one of the upstream and downstream sides of the receiver, and a liquid-side shut-off valve provided to the other of the upstream and downstream sides of the receiver. Therefore, when the first expansion valve and the liquid-side shut-off valve are fully closed, there is a risk of liquid sealing in the receiver.
  • the refrigerant circuit herein is configured with a fully-closing first expansion valve provided to one of the upstream and downstream sides of the receiver, and a fully-closing second expansion valve provided to the other of the upstream and downstream sides of the receiver.
  • first and second expansion valves are used as the first and second expansion valves and there is an increase in refrigerant pressure in the portion of the refrigerant circuit between the two expansion valves including the receiver
  • the refrigerant in the portion of the refrigerant circuit between the two expansion valves including the receiver must be able to be let to the rest of the refrigerant circuit in order to prevent liquid sealing in the receiver without providing a liquid sealing prevention pipe, even when the two expansion valves are fully closed.
  • a force thereby acts to push the needle in the needle retracting direction when the counter-pressure valve-opening pressure difference occurs, which is the difference between refrigerant pressure in a space on the needle retracting direction side of the valve seat and refrigerant pressure in a space on the needle advancing direction side of the valve seat when the valve is fully closed.
  • An air conditioning apparatus is the air conditioning apparatus according to any of the first through third aspects, wherein the urging force of the spring when the valve is fully closed is set so that the sum total of the counter-pressure valve-opening pressure difference and a maximum saturation pressure is equal to or less than the proof pressure of the receiver, the maximum saturation pressure being the refrigerant saturation pressure corresponding to the maximum value of atmospheric temperature in the location where the receiver, the first expansion valve, and the opening/closing valve are installed.
  • An air conditioning apparatus is the air conditioning apparatus according to the first aspect, wherein the refrigerant circuit further has a gas purge valve for purging refrigerant from the upper space of the receiver, and the gas purge valve is a fully-closing expansion valve that is fully closed by a needle sitting on a valve seat.
  • At least one of the first expansion valve and the gas purge valve in this case is provided to the refrigerant circuit in a first disposed state in which refrigerant from the receiver flows in from a needle advancing direction side of the valve seat, and out to a needle retracting direction side of the valve seat through a gap between the needle and the valve seat, the needle advancing direction being the direction in which the needle moves when the needle sits on the valve seat, and the needle retracting direction being the direction in which the needle moves when the needle retracts from the valve seat.
  • the refrigerant circuit herein is configured with a fully-closing first expansion valve provided to one of the upstream and downstream sides of the receiver, an opening/closing valve provided to the other of the upstream and downstream sides of the receiver, and a fully-closing gas purge valve provided to the receiver.
  • the refrigerant circuit is configured with a fully-closing first expansion valve provided to one of the upstream and downstream sides of the receiver, and a liquid-side shut-off valve provided to the other of the upstream and downstream sides of the receiver. Therefore, when the first expansion valve and the liquid-side shut-off valve are fully closed, there is a risk of liquid sealing in the receiver.
  • the fully-closing first expansion valve and/or gas purge valve herein is provided to the refrigerant circuit in the first disposed state in which refrigerant from the receiver flows in from the needle advancing direction side of the valve seat, and out to the needle retracting direction side of the valve seat through a gap between the needle and the valve seat, as described above.
  • a configuration can be achieved in which refrigerant in the portion of the refrigerant circuit between the first expansion valve, the liquid-side shut-off valve, and the gas purge valve including the receiver can be let toward the outdoor heat exchanger and/or the compressor when there is an increase in refrigerant pressure in the portion of the refrigerant circuit between the first expansion valve, the liquid-side shut-off valve, and the gas purge valve including the receiver.
  • liquid sealing in the receiver can be prevented without providing a liquid sealing prevention pipe, despite fully-closing expansion valves being used as the first expansion valve and the gas purge valve.
  • An air conditioning apparatus is the air conditioning apparatus according to the first aspect, wherein the opening/closing valve is a second expansion valve, the refrigerant circuit further has a gas purge valve for purging refrigerant from the upper space of the receiver, and the second expansion valve and the gas purge valve are fully-closing expansion valves that are each fully closed by a needle sitting on a valve seat.
  • At least one of the first expansion valve, the second expansion valve, and the gas purge valve in this case is provided to the refrigerant circuit in a first disposed state in which refrigerant from the receiver flows in from a needle advancing direction side of the valve seat, and out to a needle retracting direction side of the valve seat through a gap between the needle and the valve seat, the needle advancing direction being the direction in which the needle moves when the needle sits on the valve seat, and the needle retracting direction being the direction in which the needle moves when the needle retracts from the valve seat.
  • the first expansion valve, the second expansion valve, and/or the gas purge valve provided to the refrigerant circuit in the first disposed state has a spring for urging the needle seated on the valve seat in the needle advancing direction when the valve is fully closed, the first expansion valve, the second expansion valve, and/or the gas purge valve being configured so that the needle is released from sitting on the valve seat when the urging force of the spring in the needle advancing direction is overcome by a force pushing the needle in the needle retracting direction as generated by a counter-pressure valve-opening pressure difference, which is the difference between refrigerant pressure in a space on the needle retracting direction side of the valve seat and refrigerant pressure in a space on the needle advancing direction side of the valve seat.
  • the refrigerant circuit herein is configured with fully-closing first and second expansion valves provided to the upstream and downstream sides of the receiver, and a fully-closing gas purge valve provided to the receiver.
  • fully-closing expansion valves are used as the first expansion valve, the second expansion valve, and the gas purge valve and there is an increase in refrigerant pressure in the portion of the refrigerant circuit between the first expansion valve, the second expansion valve, and the gas purge valve including the receiver
  • the refrigerant in the portion of the refrigerant circuit between the first expansion valve, the second expansion valve, and the gas purge valve including the receiver must be able to be let to the rest of the refrigerant circuit in order to prevent liquid sealing in the receiver without providing a liquid sealing prevention pipe, even when the first expansion valve, the second expansion valve, and the gas purge valve are fully closed.
  • At least one of the first expansion valve, the second expansion valve, and the gas purge valve is provided to the refrigerant circuit in the first disposed state in which refrigerant from the receiver flows in from the needle advancing direction side of the valve seat, and out to the needle retracting direction side of the valve seat through a gap between the needle and the valve seat, as described above.
  • the force pushing the needle in the needle retracting direction due to this counter-pressure valve-opening pressure difference is utilized to provide a configuration in which the first expansion valve, the second expansion valve, and/or the gas purge valve provided to the refrigerant circuit in the first disposed state is provided with the spring for urging the needle seated on the valve seat in the needle advancing direction when the valve is fully closed, and when the force pushing the needle in the needle retracting direction due to the counter-pressure valve-opening pressure difference overcomes the urging force of the spring in the needle advancing direction, the needle is released from sitting on the valve seat.
  • liquid sealing in the receiver can be prevented without providing a liquid sealing prevention pipe, despite fully-closing expansion valves being used as the first expansion valve, the second expansion valve, and the gas purge valve.
  • the urging force of the spring when the valve is fully closed is set herein so that the sum total of the counter-pressure valve-opening pressure difference and the maximum saturation pressure is equal to or less than the proof pressure of the receiver, the maximum saturation pressure being the refrigerant saturation pressure corresponding to the maximum value of atmospheric temperature in the location where the first expansion valve, the opening/closing valve, and the gas purge valve are installed, as described above.
  • the refrigerant in the portion of the refrigerant circuit between the first expansion valve, the opening/closing valve, and the gas purge valve including the receiver can be let toward the outdoor heat exchanger, the indoor heat exchanger, and/or the compressor before the proof pressure of the receiver is exceeded, and liquid sealing in the receiver can be prevented.
  • the proof pressure herein is obtained on the basis of the design pressure of the receiver, it is possible to appropriately set the counter-pressure valve-opening pressure difference of the first expansion valve, the second expansion valve, and/or the gas purge valve provided in the first disposed state, i.e., to appropriately set the urging force of the spring when the valve is fully closed.
  • An air conditioning apparatus is the air conditioning apparatus according to the first or fifth aspect, wherein the opening/closing valves are a second expansion valve and a liquid-side shut-off valve connected between the second expansion valve and the indoor heat exchanger, and the second expansion valve is a fully-closing expansion valve that is fully closed by a needle sitting on a valve seat.
  • the second expansion valve herein is provided to the refrigerant circuit in a second disposed state in which refrigerant from the receiver flows in from the needle retracting direction side of the valve seat, and out to the needle advancing direction side of the valve seat through a gap between the needle and the valve seat.
  • the refrigerant in the portion of the refrigerant circuit between the liquid-side shut-off valve and the second expansion valve must be able to be let to the rest of the refrigerant circuit in order to make liquid sealing preventable in the portion between the liquid-side shut-off valve and the second expansion valve.
  • the second expansion valve is provided to the refrigerant circuit in the second disposed state, in which refrigerant from the receiver flows in from the needle retracting direction side of the valve seat, and out to the needle advancing direction side of the valve seat through the gap between the needle and the valve seat.
  • a force will thereby act to push the needle in the needle retracting direction when the counter-pressure valve-opening pressure difference occurs, which is the difference between refrigerant pressure in the space on the needle retracting direction side of the valve seat and refrigerant pressure in the space on the needle advancing direction side of the valve seat when the second expansion valve is fully closed.
  • the force pushing the needle in the needle retracting direction due to this counter-pressure valve-opening pressure difference is utilized to provide a configuration in which the second expansion valve provided to the refrigerant circuit in the second disposed state is provided with the spring for urging the needle seated on the valve seat in the needle advancing direction when the valve is fully closed, and when the force pushing the needle in the needle retracting direction due to the counter-pressure valve-opening pressure difference overcomes the urging force of the spring in the needle advancing direction, the needle is released from sitting on the valve seat.
  • liquid sealing in the receiver can be prevented without providing a liquid sealing prevention pipe, and liquid sealing between the liquid-side shut-off valve and the second expansion valve can be prevented.
  • An air conditioning apparatus is the air conditioning apparatus according to the tenth aspect, wherein the urging force of the spring of the second expansion valve when the valve is fully closed is set so that the sum total of a maximum saturation pressure and the counter-pressure valve-opening pressure difference of the second expansion valve is equal to or less than the minimum value of the proof pressures of the components constituting the portion of the refrigerant circuit from the second expansion valve to the liquid-side shut-off valve, the maximum saturation pressure being the refrigerant saturation pressure corresponding to the maximum value of atmospheric temperature in the location where the second expansion valve and the liquid-side shut-off valve are installed.
  • the urging force of the spring when the valve is fully closed is set herein so that the sum total of the counter-pressure valve-opening pressure difference and the maximum saturation pressure is equal to or less than the minimum value of the proof pressures of the components constituting the portion of the refrigerant circuit from the second expansion valve to the liquid-side shut-off valve, the maximum saturation pressure being the refrigerant saturation pressure corresponding to the maximum value of atmospheric temperature in the location where the second expansion valve is installed, as described above.
  • the refrigerant in the portion of the refrigerant circuit between the liquid-side shut-off valve and the second expansion valve can be let toward the receiver before the proof pressures of the components constituting the portion of the refrigerant circuit from the second expansion valve to the liquid-side shut-off valve are exceeded, and liquid sealing between the liquid-side shut-off valve and the second expansion valve can be prevented.
  • the refrigerant let toward the receiver will cause a pressure increase in the receiver, but because the first expansion valve (and the first expansion valve and/or the gas purge valve when there is also a gas purge valve) is provided in the first disposed state, the refrigerant will be let toward the outdoor heat exchanger (toward the outdoor heat exchanger and/or the compressor when there is also a gas purge valve) before the proof pressure of the receiver is exceeded.
  • liquid sealing between the liquid-side shut-off valve and the second expansion valve can be appropriately prevented while taking into account the proof pressures of the components constituting the portion of the refrigerant circuit from the second expansion valve to the liquid-side shut-off valve.
  • An air conditioning apparatus is the air conditioning apparatus according to the eleventh aspect, wherein the proof pressures of the components constituting the portion of the refrigerant circuit from the second expansion valve to the liquid-side shut-off valve are pressure values obtained by multiplying the design pressures of the components constituting the portion of the refrigerant circuit from the second expansion valve to the liquid-side shut-off valve by a safety factor.
  • the proof pressures herein are obtained on the basis of the design pressures of the components constituting the portion of the refrigerant circuit from the second expansion valve to the liquid-side shut-off valve, it is possible to appropriately set the counter-pressure valve-opening pressure difference of the second expansion valve provided in the second disposed state, i.e., to appropriately set the urging force of the spring when the valve is fully closed.
  • the four-way switching valve 22 performs a switch that causes the outdoor heat exchanger 23 to function as an evaporator of refrigerant that has radiated heat in the indoor heat exchanger 41, and causes the indoor heat exchanger 41 to function as a heat radiator of refrigerant that has been compressed in the compressor 21, and thereby switches into an air-warming cycle state.
  • the four-way switching valve 22 performs a switch that interconnects the second port 22b and the fourth port 22d, and interconnects the first port 22a and the third port 22c.
  • the outdoor unit 2 has an outdoor-side controller 38 for controlling the actions of the components constituting the outdoor unit 2.
  • the outdoor-side controller 38 which has a microcomputer, memory, and/or the like provided in order to control the outdoor unit 2, is designed to be capable of exchanging control signals and the like with the indoor unit 4 via the transmission line 8a.
  • the refrigerant circuit 10 of the air-conditioning apparatus 1 is configured from the connection between the outdoor unit 2, the indoor unit 4, and the refrigerant communication pipes 5, 6.
  • the air conditioning apparatus 1 is designed so that switching the four-way switching valve 22 to the air-cooling cycle state causes the air-cooling operation to be performed, in which refrigerant is circulated sequentially through the compressor 21, the outdoor heat exchanger 23, the first expansion valve 24, the receiver 25, the second expansion valve 26 (an opening/closing valve), the liquid-side shut-off valve 27 (an opening/closing valve) and the indoor heat exchanger 41.
  • the air conditioning apparatus 1 is also designed so that switching the four-way switching valve 22 to the air-warming cycle state causes the air-warming operation to be performed, in which refrigerant is circulated sequentially through the compressor 21, the indoor heat exchanger 41, the liquid-side shut-off valve 27 (an opening/closing valve), the second expansion valve 26 (an opening/closing valve), the receiver 25, the first expansion valve 24, and the outdoor heat exchanger 23.
  • the configuration herein is capable of switching between the air-cooling operation and the air-warming operation, but another option is a configuration that does not have a four-way switching valve and that is capable of only an air-cooling operation or only an air-warming operation.
  • the four-way switching valve 22 is switched to the air-warming cycle state (the state shown by the dashed lines in FIG. 1 ).
  • low-pressure gas refrigerant in the refrigeration cycle is drawn into the compressor 21 and discharged after being compressed to a high pressure.
  • the high-pressure gas refrigerant discharged from the compressor 21 is sent through the four-way switching valve 22, the gas-side shut-off valve 28, and the gas refrigerant communication pipe 6 to the indoor heat exchanger 41.
  • the high-pressure gas refrigerant sent to the indoor heat exchanger 41 undergoes heat exchange with indoor air supplied as a cooling source by the indoor fan 42 and radiates heat in the indoor heat exchanger 41, becoming high-pressure liquid refrigerant.
  • the indoor air is thereby heated and then supplied into the room, whereby air-warming of the room interior is performed.
  • the high-pressure liquid refrigerant that has radiated heat in the indoor heat exchanger 41 is sent through the liquid refrigerant communication pipe 5 and the liquid-side shut-off valve 27 to the second expansion valve 26.
  • the high-pressure liquid refrigerant sent to the second expansion valve 26 is depressurized to an intermediate pressure in the refrigeration cycle by the second expansion valve 26, becoming intermediate-pressure, gas-liquid two-phase refrigerant.
  • the inteimediate-pressure, gas-liquid two-phase refrigerant sent to the first expansion valve 24 is depressurized to a low pressure in the refrigeration cycle by the first expansion valve 24, becoming low-pressure, gas-liquid two-phase refrigerant.
  • the low-pressure, gas-liquid two-phase refrigerant depressurized by the first expansion valve 24 is sent to the outdoor heat exchanger 23.
  • the low-pressure, gas-liquid two-phase refrigerant sent to the outdoor heat exchanger 23 undergoes heat exchange with outdoor air supplied as a heating source by the outdoor fan 36 and evaporates in the outdoor heat exchanger 23, becoming low-pressure gas refrigerant.
  • the low-pressure refrigerant evaporated in the outdoor heat exchanger 23 is drawn through the four-way switching valve 22 back into the compressor 21.
  • the four-way switching valve 22 is switched to the air-cooling cycle state (the state shown by the solid lines in FIG. 1 ).
  • the high-pressure liquid refrigerant sent to the first expansion valve 24 is depressurized to an intermediate pressure in the refrigeration cycle by the first expansion valve 24, becoming intermediate-pressure, gas-liquid two-phase refrigerant.
  • the intermediate-pressure, gas-liquid two-phase refrigerant sent to the second expansion valve 26 is depressurized to a low pressure in the refrigeration cycle by the second expansion valve 26, becoming low-pressure, gas-liquid two-phase refrigerant.
  • the low-pressure, gas-liquid two-phase refrigerant depressurized by the second expansion valve 26 is sent through the liquid-side shut-off valve 27 and the liquid refrigerant communication pipe 5 to the indoor heat exchanger 41.
  • the valve body 51 herein is a substantially tubular member extending vertically (i.e., in the direction in which the needle 61 moves), in which a valve chamber 52 is formed.
  • the valve chamber 52 has an upper valve chamber 52a large in diameter, and a lower valve chamber 52b small in diameter and positioned beneath the upper valve chamber 52a.
  • Also formed in the valve body 51 are a first refrigerant port 53 opening into the side of the valve chamber 52 (the upper valve chamber 52a herein), and a second refrigerant port 54 opening into the bottom of the valve chamber 52 (the lower valve chamber 52b herein).
  • the valve seat 55 is also provided in the valve body 51. Specifically, the valve seat 55 is provided in the valve body 51 so as to partition the upper valve chamber 52a and the lower valve chamber 52b.
  • the case 71 herein is a substantially tubular member of which the upper end is closed.
  • the case 71 is secured to the upper end of the valve body 51 via a securing metal fitting or the like (not shown).
  • a substantially tubular sleeve 72 extending downward is provided to the inner surface of the upper end of the case 71.
  • the upper end of the valve shaft 64 is inserted into the internal peripheral side of the sleeve 72 so as to be able to rotate and move vertically (i.e., in the direction in which the needle moves).
  • the external peripheral surface of the rotor 81 faces the internal peripheral surface of the case 71 with a slight gap in between.
  • a stator 82 composed of an electromagnet is provided to a position of facing the rotor 81 on the external peripheral side of the case 71.
  • the first expansion valve 24 is provided to the refrigerant circuit 10 in a first disposed state, in which refrigerant from the receiver 25 flows in from the needle advancing direction side of the valve seat 55 (the lower side of the valve seat 55 herein), through the gap between the needle 61 and the valve seat 55, and out to the needle retracting direction side of the valve seat 55 (the upper side of the valve seat 55 herein) (see FIGS. 2 and 3 ).
  • first liquid refrigerant pipe 35a for connecting with the outdoor heat exchanger 23 is connected to the first refrigerant port 53 of the first expansion valve 24, and the second liquid refrigerant pipe 35b for connecting with the receiver 25 is connected to the second refrigerant port 54 of the first expansion valve 24, as shown in FIGS. 2 and 3 .
  • the force Fu pushing the needle 61 in the needle retracting direction due to this counter-pressure valve-opening pressure difference ⁇ P is utilized to provide a configuration in which the first expansion valve 24 provided to the refrigerant circuit 10 in the first disposed state is provided with the spring 62 for urging the needle 61 seated on the valve seat 55 in the needle advancing direction (downward herein) when the valve is fully closed, and when the force Fu pushing the needle 61 in the needle retracting direction due to the counter-pressure valve-opening pressure difference ⁇ P overcomes the urging force Fd of the spring 62 in the needle advancing direction, the needle 61 is released from sitting on the valve seat 55 (see FIGS. 4 and 5 ).
  • the needle 61 comes to be seated on the valve seat 55 while the spring 62 contracts to less than its free length but could still contract further (this state is referred to below as the "counter-pressure valve-opening inactive state").
  • the spring 62 thereby generates a force Fd urging the needle 61 seated on the valve seat 55 in the needle advancing direction, and the needle 61 is pushed against the valve seat 55 by the urging force Fd of the spring 62.
  • the length of the spring 62 contracts from the length L0 in the counter-pressure valve-opening inactive state to the length L in the counter-pressure valve-opening active state.
  • the refrigerant in the portion of the refrigerant circuit 10 between the two expansion valves 24, 26 including the receiver 25 can thereby be let toward the outdoor heat exchanger 23 (refer to the arrow indicating refrigerant flow in FIG. 5 ).
  • the urging force Fd of the spring 62 when the valve is fully closed is herein set so that the sum total of the counter-pressure valve-opening pressure difference ⁇ P and a maximum saturation pressure Psm is equal to or less than the proof pressure Prm of the receiver 25, the maximum saturation pressure Psm being the refrigerant saturation pressure corresponding to the maximum value of atmospheric temperature in the location where the first and second expansion valves 24, 26 (the outdoor unit 2 herein) are installed.
  • the maximum saturation pressure Psm is a value obtained by converting the maximum atmospheric temperature (e.g., approximately 50°C) that could be assumed in the location where the first and second expansion valves 24, 26 (the outdoor unit 2 herein) are installed to a refrigerant saturation pressure.
  • the proof pressure Prm is the proof pressure of the receiver 25, which has the lowest proof pressure among the first expansion valve 24, the receiver 25, and the second expansion valve 26 as the components constituting the portion of the refrigerant circuit 10 between the two expansion valves 24, 26 including the receiver 25.
  • the proof pressure Prm of the receiver 25 herein is obtained by multiplying the design pressure of the receiver 25 by a safety factor (e.g., approximately 1.5 times corresponding to a proof test pressure).
  • the spring constant and the spring length L0 in the counter-pressure valve-opening inactive state are set so that the urging force Fd in the counter-pressure valve-opening inactive state is equal to or less than a force Fum pushing the needle 61 in the needle retracting direction, generated when the needle 61 is assumed to be subjected to a pressure difference that is the proof pressure Prm of the receiver 25 minus the maximum saturation pressure Psm.
  • This pressure difference corresponding to the urging force Fd in the counter-pressure valve-opening inactive state is designated as the counter-pressure valve-opening pressure difference ⁇ P.
  • the proof pressure Prm of the receiver 25 herein is obtained on the basis of the design pressure of the receiver 25 as described above, the counter-pressure valve-opening pressure difference ⁇ P, i.e., the urging force Fd of the spring while the valve is fully closed can be appropriately set.
  • the refrigerant in the portion of the refrigerant circuit 10 between the two expansion valves 24, 26 including the receiver 25 can be let toward the outdoor heat exchanger 23 before the proof pressure Prm of the receiver 25 is exceeded, and liquid sealing in the receiver 25 can be prevented. Due to the refrigerant in the portion of the refrigerant circuit 10 between the two expansion valves 24, 26 including the receiver 25 being let toward the outdoor heat exchanger 23, when there is a decrease in the refrigerant pressure in the portion of the refrigerant circuit 10 between the two expansion valves 24, 26 including the receiver 25, less force Fu pushing the needle 61 in the needle retracting direction is generated by the counter-pressure valve-opening pressure difference ⁇ P, and the first expansion valve 24 returns to the counter-pressure valve-opening inactive state. Instances of the first expansion valve 24 going into the counter-pressure valve-opening active state can thereby be kept to the necessary minimum.
  • liquid sealing in the receiver 25 can be prevented without providing a liquid sealing prevention pipe, despite fully-closing expansion valves being used as the first expansion valve 24 and the second expansion valve 26.
  • liquid sealing in the receiver 25 can be appropriately prevented while taking the proof pressure Prm of the receiver 25 into account.
  • the second expansion valve 26 is provided to the refrigerant circuit 10 in a second disposed state, in which refrigerant from the receiver 25 flows in from the needle retracting direction side of the valve seat 55 (the upper side of the valve seat 55 herein), through the gap between the needle 61 and the valve seat 55, and out to the needle advancing direction side of the valve seat 55 (the lower side of the valve seat 55 herein) (see FIGS. 2 and 3 ).
  • the third liquid refrigerant pipe 35c for connecting with the receiver 25 is connected to the first refrigerant port 53 of the second expansion valve 26, and the fourth liquid refrigerant pipe 35d for connecting with the liquid-side shut-off valve 27 is connected to the second refrigerant port 54 of the second expansion valve 26, as shown in FIGS. 2 and 3 .
  • the force Fu pushing the needle 61 in the needle retracting direction due to this counter-pressure valve-opening pressure difference ⁇ P is utilized to provide a configuration in which the second expansion valve 26 provided to the refrigerant circuit 10 in the second disposed state is provided with the spring 62 for urging the needle 61 seated on the valve seat 55 in the needle advancing direction (downward herein) when the valve is fully closed, and when the force Fu pushing the needle 61 in the needle retracting direction due to the counter-pressure valve-opening pressure difference ⁇ P overcomes the urging force Fd of the spring 62 in the needle advancing direction, the needle 61 is released from sitting on the valve seat 55 (see FIGS. 4 and 5 ).
  • the needle 61 comes to be seated on the valve seat 55 while the spring 62 contracts to less than its free length but could still contract further (this state is referred to below as the "counter-pressure valve-opening inactive state").
  • the spring 62 thereby generates a force Fd urging the needle 61 seated on the valve seat 55 in the needle advancing direction, and the needle 61 is pushed against the valve seat 55 by the urging force Fd of the spring 62.
  • the urging force Fd of the spring 62 while the valve is fully closed is herein set so that the sum total of the counter-pressure valve-opening pressure difference ⁇ P and a maximum saturation pressure Psm is equal to or less than the minimum proof pressure value Phm of the components constituting the portion of the refrigerant circuit 10 from the second expansion valve 26 to the liquid-side shut-off valve 27, the maximum saturation pressure Psm being the refrigerant saturation pressure corresponding to the maximum value of atmospheric temperature in the location where the second expansion valve 26 (the outdoor unit 2 herein) is installed.
  • the refrigerant in the portion of the refrigerant circuit 10 between the liquid-side shut-off valve 27 and the second expansion valve 26 can be let toward the receiver 25 before the pressure exceeds the proof pressures of the components constituting the portion of the refrigerant circuit 10 from the second expansion valve 26 to the liquid-side shut-off valve 27, and liquid sealing between the liquid-side shut-off valve 27 and the second expansion valve 26 can be prevented.
  • the refrigerant let toward the receiver 25 will cause a pressure increase in the receiver 25, but because the first expansion valve 24 is provided in the first disposed state, the refrigerant will be let toward the outdoor heat exchanger 23 before the proof pressure Prm of the receiver 25 is exceeded.
  • the air conditioning apparatus 1 of the above embodiment is configured with the fully-closing first expansion valve 24 and second expansion valve 26 (an opening/closing valve) provided on the upstream and downstream sides of the receiver 25, wherein the first expansion valve 24 is provided in a first disposed state and the second expansion valve 26 is provided in a second disposed state in order to prevent liquid sealing in the receiver 25 and liquid sealing between the liquid-side shut-off valve 27 (an opening/closing valve) and the second expansion valve 26.
  • the first expansion valve 24 and the second expansion valve 26 can also both be provided in the first disposed state as shown in FIG. 7 .
  • the first and second expansion valves 24, 26 are provided in the first disposed state and there is an increase in refrigerant pressure in the portion of the refrigerant circuit 10 between the two expansion valves 24, 26 including the receiver 25, the refrigerant in the portion of the refrigerant circuit 10 between the two expansion valves 24, 26 including the receiver 25 can be let towards the outdoor heat exchanger 23 and the indoor heat exchanger 41 to prevent liquid sealing in the receiver 25.
  • liquid sealing in the receiver 25 can be prevented without providing a liquid sealing prevention pipe, despite fully-closing expansion valves being used as the first expansion valve 24 and the second expansion valve 26.
  • the first expansion valve 24 can be provided in the first disposed state
  • the second expansion valve 26 and the gas purge valve 30a can be provided in the second disposed state, as shown in FIG. 10 .
  • the maximum saturation pressure used to set the urging force of the spring 62 herein is the refrigerant saturation pressure corresponding to the maximum value of atmospheric temperature in the location (the outdoor unit 2 herein) where the receiver 25, the first expansion valve 24, the second expansion valve 26, and the gas purge valve 30a are installed.
  • the refrigerant in the portion of the refrigerant circuit 10 between the two expansion valves 24, 26 and the gas purge valve 30a including the receiver 25 can be let towards the outdoor heat exchanger 23 to prevent liquid sealing in the receiver 25.
  • liquid sealing in the receiver 25 can be prevented and liquid sealing between the liquid-side shut-off valve 27 (an opening/closing valve) and the second expansion valve 26 can be prevented because the second expansion valve 26 is provided in the second disposed state.
  • Liquid sealing in the receiver 25 can also be prevented herein without providing a liquid sealing prevention pipe and liquid sealing between the liquid-side shut-off valve 27 (an opening/closing valve) and the second expansion valve 26 can be prevented by providing the first expansion valve 24 and/or the gas purge valve 30a in the first disposed state and providing the second expansion valve 26 in the second disposed state.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)
  • Safety Valves (AREA)
  • Air Conditioning Control Device (AREA)
EP14810377.3A 2013-06-11 2014-06-02 Climatiseur Active EP3009773B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013122800 2013-06-11
PCT/JP2014/064613 WO2014199855A1 (fr) 2013-06-11 2014-06-02 Climatiseur

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EP3009773A1 true EP3009773A1 (fr) 2016-04-20
EP3009773A4 EP3009773A4 (fr) 2016-05-18
EP3009773B1 EP3009773B1 (fr) 2018-04-04

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JP (1) JP5862704B2 (fr)
CN (1) CN105308400B (fr)
AU (1) AU2014279254C1 (fr)
ES (1) ES2673875T3 (fr)
WO (1) WO2014199855A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE102015114309A1 (de) * 2015-08-28 2017-03-02 Halla Visteon Climate Control Corporation Bidirektionales elektronisches Expansionsorgan

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7123020B2 (ja) * 2019-09-03 2022-08-22 株式会社鷺宮製作所 電動弁及び冷凍サイクルシステム
CN111678270A (zh) * 2020-06-11 2020-09-18 南京航空航天大学 一种带自力式容量调节储液器的热管与蒸气压缩复合系统

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WO2007083794A1 (fr) * 2006-01-20 2007-07-26 Sanyo Electric Co., Ltd. Climatiseur
WO2009069257A1 (fr) * 2007-11-30 2009-06-04 Daikin Industries, Ltd. Dispositif de congélation

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JPH10132393A (ja) 1996-10-31 1998-05-22 Daikin Ind Ltd 冷凍装置
JP3487241B2 (ja) * 1999-10-29 2004-01-13 ダイキン工業株式会社 冷凍装置
JP2005121333A (ja) * 2003-10-20 2005-05-12 Hitachi Ltd 空気調和装置
JP4940832B2 (ja) * 2006-08-30 2012-05-30 ダイキン工業株式会社 冷凍装置
CN105157266B (zh) * 2009-10-23 2020-06-12 开利公司 制冷剂蒸气压缩系统的运行
JP6174314B2 (ja) * 2012-12-14 2017-08-02 シャープ株式会社 冷凍システム装置

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WO2007083794A1 (fr) * 2006-01-20 2007-07-26 Sanyo Electric Co., Ltd. Climatiseur
WO2009069257A1 (fr) * 2007-11-30 2009-06-04 Daikin Industries, Ltd. Dispositif de congélation

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015114309A1 (de) * 2015-08-28 2017-03-02 Halla Visteon Climate Control Corporation Bidirektionales elektronisches Expansionsorgan
DE102015114309B4 (de) * 2015-08-28 2020-01-30 Hanon Systems Bidirektionales elektronisches Expansionsorgan

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WO2014199855A1 (fr) 2014-12-18
CN105308400A (zh) 2016-02-03
AU2014279254B2 (en) 2016-11-24
AU2014279254C1 (en) 2017-03-23
EP3009773B1 (fr) 2018-04-04
AU2014279254A1 (en) 2016-02-04
AU2014279254B9 (en) 2016-12-01
ES2673875T3 (es) 2018-06-26
CN105308400B (zh) 2017-10-27
EP3009773A4 (fr) 2016-05-18
JP5862704B2 (ja) 2016-02-16
JP2015017795A (ja) 2015-01-29

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