EP3534088B1 - Climatiseur - Google Patents

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Publication number
EP3534088B1
EP3534088B1 EP16920284.3A EP16920284A EP3534088B1 EP 3534088 B1 EP3534088 B1 EP 3534088B1 EP 16920284 A EP16920284 A EP 16920284A EP 3534088 B1 EP3534088 B1 EP 3534088B1
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EP
European Patent Office
Prior art keywords
pressure
refrigerant
valve
air conditioner
valve body
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.)
Active
Application number
EP16920284.3A
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German (de)
English (en)
Other versions
EP3534088A1 (fr
EP3534088A4 (fr
Inventor
Yusuke Tashiro
Komei NAKAJIMA
Masakazu Sato
Yusuke Adachi
Yasuhide Hayamaru
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP3534088A1 publication Critical patent/EP3534088A1/fr
Publication of EP3534088A4 publication Critical patent/EP3534088A4/fr
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Publication of EP3534088B1 publication Critical patent/EP3534088B1/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
    • F25B1/00—Compression machines, plants or systems with non-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
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F25B41/335—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant via diaphragms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using 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
    • 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
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel 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
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/191—Pressures near an expansion valve

Definitions

  • the present invention relates to air conditioners.
  • Air conditioners that reduce refrigerant consumption with the use of low global warming potential (GWP) refrigerant are desired in consideration of global environment.
  • R32 Used as the refrigerant enabling such air conditioners that reduce refrigerant consumption with the use of low GWP refrigerant is R32.
  • R32 is refrigerant which has a small politropic exponent and whose temperature easily increases when discharged from a compressor. The use of R32 as refrigerant thus easily increases the temperature of the refrigerant discharged from the compressor at high outside temperature and at high condensation temperature. Since an increase in the temperature of the refrigerant discharged from the compressor may lead to a failure of the compressor, the temperature of the refrigerant discharged from the compressor is desired not to exceed a set temperature in order to prevent a failure of the compressor.
  • a linear expansion valve (LEV) is used to adjust the temperature of the refrigerant discharged from a compressor.
  • LEV linear expansion valve
  • a microcomputer controls the degree of opening of the LEV based on a signal from a thermistor that has detected the temperature of the refrigerant discharged from the compressor to adjust the temperature of the refrigerant discharged from the compressor not to exceed the set temperature.
  • JP 2016-109356 A discloses an air conditioner that uses R32 as refrigerant and includes an LEV.
  • JP H09 133436 A discloses an expansion valve having a reference pressure chamber connected to a valve stem, which is seated in a valve seat.
  • the valve stem is biased by a spring. The valve opens and closes depending on the pressure in the gas inlet, the gas outlet as well as in the reference chamber.
  • JP 2004 036997 A discloses a further expansion valve with an inlet passage, an outlet passage, a valve seat and a valve body, wherein the valve body moves relative to the valve seat and changes the communication state of the inlet passage and the outlet passage.
  • the valve body is biased via a sensitive element, in which an incapsulation substance is incapsulated and which controls the emotion of the valve body upon sensing the temperature of the refrigerant a high pressure line.
  • WO 01/06183 A1 discloses a further refrigerant cycle with an inlet and an outlet and a valve stem and a valve seat arranges arranged between the inlet and the outlet.
  • the valve stem is biased via a sensing element filled with inert gas or CO 2 .
  • the air conditioner disclosed in the above literature has a long response time of the temperature of the refrigerant discharged from the compressor with respect to the adjustment of the degree of opening of the LEV. Consequently, the adjustment of the degree of opening of the LEV may not keep up with an increase in the temperature of the refrigerant discharged from the compressor, allowing the temperature of the refrigerant discharged from the compressor to exceed the set temperature. A reduced amount of refrigerant may lead to a shorter response time of the temperature of the refrigerant discharged from the compressor with respect to the adjustment of the degree of opening of the LEV.
  • the present invention has been made in view of the above problem and has an object to provide an air conditioner that can suppress an increase in the temperature of refrigerant discharged from a compressor and reduce refrigerant consumption with the use of low GWP refrigerant.
  • An air conditioner of the present invention is defined by appended independent claim 1.
  • the air conditioner of the present invention sets the pressure in the pressure reference chamber to the pressure in the flow path where the temperature of the refrigerant discharged from the compressor is a set temperature, and accordingly can increase the degree of opening of the valve portion when the pressure in the flow path is higher than the pressure in the pressure reference chamber, thus suppressing the temperature of the refrigerant discharged from the compressor exceeding the set temperature. Also, the degree of opening of the valve portion is adjusted before the temperature of the refrigerant discharged from the compressor exceeds the set temperature, thus suppressing the generation of hunting.
  • R32 is low GWP refrigerant. Therefore, an air conditioner that reduces refrigerant consumption with the use of low GWP refrigerant can be achieved.
  • Air conditioner 10 of the present embodiment is a device dedicated to cooling. That is to say, air conditioner 10 of the present embodiment has a cooling function and does not have a heating function.
  • Air conditioner 10 of the present embodiment mainly includes a compressor 1, a condenser 2, a pressure-regulating valve 3, an evaporator 4, a blower for condenser 5, a blower for evaporator 6, pipes PI1 to PI4, and refrigerant.
  • Compressor 1, condenser 2, pressure-regulating valve 3, and blower for condenser 5 are accommodated in an outdoor unit 11.
  • Evaporator 4 and blower for evaporator 6 are accommodated in an indoor unit 12.
  • Refrigerant circuit 13 has compressor 1, condenser 2, pressure-regulating valve 3, and evaporator 4.
  • Compressor 1, condenser 2, pressure-regulating valve 3, and evaporator 4 communicated with each other through pipes PI1 to PI4 constitute refrigerant circuit 13.
  • compressor 1 and condenser 2 are connected to each other by pipe PI1.
  • Condenser 2 and pressure-regulating valve 3 are connected to each other by pipe PI2.
  • Pressure-regulating valve 3 and evaporator 4 are connected to each other by pipe PI3.
  • Evaporator 4 and compressor 1 are connected to each other by pipe PI4.
  • Refrigerant circuit 13 is configured to allow refrigerant to circulate therethrough in the order of compressor 1, pipe PI1, condenser 2, pipe PI2, pressure-regulating valve 3, pipe PI3, evaporator 4, and pipe PI4. That is to say, refrigerant flows through refrigerant circuit 13 in the order of compressor 1, condenser 2, pressure-regulating valve 3, and evaporator 4.
  • Refrigerant is R32.
  • the amount of the refrigerant flowing through refrigerant circuit 13 is preferably 300 g or more and 500 g or less.
  • Compressor 1 is configured to compress refrigerant. Compressor 1 is also configured to compress the sucked refrigerant and discharge the compressed refrigerant. Compressor 1 is configured to have a variable capacity. Compressor 1 of the present embodiment is configured to variably control the number of rotations. Specifically, the drive frequency of compressor 1 is changed based on an instruction from a controller (not shown), so that the number of rotations of compressor 1 is adjusted. This changes the capacity of compressor 1.
  • the capacity of compressor 1 is an amount by which refrigerant is fed per unit time. That is to say, compressor 1 can perform a high-capacity operation and a low-capacity operation.
  • an operation is performed by setting the drive frequency of compressor 1 high to increase the flow rate of refrigerant circulating through refrigerant circuit 13.
  • an operation is performed by setting the drive frequency of compressor 1 low to reduce the flow rate of refrigerant circulating through refrigerant circuit 13.
  • Condenser 2 is configured to condense the refrigerant compressed by compressor 1.
  • Condenser 2 is an air-heat exchanger formed of a pipe and a fin.
  • Pressure-regulating valve 3 is configured to decompress the refrigerant condensed by condenser 2.
  • Pressure-regulating valve 3 has the function as an expansion valve.
  • Pressure-regulating valve 3 is also a mechanical pressure control valve.
  • Pressure-regulating valve 3 is also configured to adjust the flow rate of the refrigerant flowing through pressure-regulating valve 3.
  • the flow rate of the refrigerant flowing through pressure-regulating valve 3 is a flow rate per unit time.
  • Evaporator 4 is configured to evaporate the refrigerant decompressed by pressure-regulating valve 3.
  • Evaporator 4 is an air-heat exchanger formed of a pipe and a fin.
  • Blower for condenser 5 is configured to adjust a heat exchange amount between the outdoor air and refrigerant in condenser 2.
  • Blower for condenser 5 is formed of a fan 5a and a motor 5b.
  • Motor 5b may be configured to rotate fan 5a such that the number of rotations of fan 5a is variable.
  • Motor 5b may also be configured to rotate fan 5a such that the number of rotations of fan 5a is constant.
  • Blower for evaporator 6 is configured to adjust a heat exchange amount between the indoor air and refrigerant in evaporator 4.
  • Blower for evaporator 6 is formed of a fan 6a and a motor 6b.
  • Motor 6b may be configured to rotate fan 6a such that the number of rotations of fan 6a is variable.
  • Motor 6b may be configured to rotate fan 6a such that the number of rotations of fan 6a is constant.
  • Pressure-regulating valve 3 includes a case 31, a diaphragm 32, a flow path 33, a valve portion 34, a spring 35, and a partition member 36. Pressure-regulating valve 3 is configured to adjust the degree of opening of valve portion 34 to adjust the flow rate of the refrigerant flowing through flow path 33.
  • Diaphragm 32 is attached to the inner side of case 31 to partition the interior of case 31.
  • Case 31 has a first chamber S1 and a second chamber S2 partitioned by diaphragm 32.
  • First chamber S1 has flow path 33 which causes the refrigerant flowing from condenser 2 to flow to evaporator 4.
  • first chamber S1 has a flow inlet portion 31a and a flow outlet portion 31b.
  • Flow inlet portion 31a is connected to pipe PI2.
  • Flow outlet portion 31b is connected to pipe PI3.
  • First chamber S1 is configured to allow the refrigerant flowing through the refrigerant circuit to flow from pipe PI2 through flow inlet portion 31a into first chamber S1 and then flow through outlet portion 31b to pipe PI3. That is to say, the refrigerant flowing through the refrigerant circuit flows into first chamber S1 from flow inlet portion 31a and flows out of flow outlet portion 31b, as indicated by arrows A1 in Fig. 2 .
  • the path from flow inlet portion 31a to flow outlet portion 31b forms flow path 33 for refrigerant.
  • the pressure of first chamber S1 is a pressure of the refrigerant in flow path 33. Since the pressure of first chamber S1 is a pressure of the refrigerant flowing thereinto from condenser 2, it is a pressure of high-pressure-side refrigerant flowing through refrigerant circuit 13. Pressure-regulating valve 3 is accordingly a high-pressure pressure-regulating valve.
  • Second chamber S2 forms a pressure reference chamber S2.
  • Pressure reference chamber S2 is partitioned from flow path 33.
  • Pressure reference chamber S2 is filled with inert gas.
  • Pressure reference chamber S2 is hermetically sealed while being filled with inert gas.
  • the pressure in pressure reference chamber S2 is a pressure of the inert gas.
  • the inert gas is, for example, nitrogen or helium. Nitrogen is advantageous in low cost. Helium is advantageous in high level of safety.
  • the pressure in pressure reference chamber S2 is, for example, 3 MPa or more and 4 MPa or less.
  • Diaphragm 32 is configured to deform in the direction indicated by a double-pointed arrow A2 in Fig. 2 due to a pressure difference between the pressure of first chamber S1 and the pressure of second chamber S2, that is, a pressure difference between the pressure of the refrigerant in flow path 33 and the pressure of the inert gas in pressure reference chamber S2.
  • diaphragm 32 is configured to curve in a projecting manner toward pressure reference chamber S2 when the pressure of the refrigerant in flow path 33 is higher than the pressure of the inert gas in pressure reference chamber S2.
  • diaphragm 32 is configured to be planar when the pressure of the refrigerant in flow path 33 is equal to or lower than the pressure of the inert gas in pressure reference chamber S2. That is to say, in this case, diaphragm 32 does not curve in a projecting manner toward pressure reference chamber S2.
  • Valve portion 34, spring 35, and partition member 36 are disposed in first chamber S1.
  • Partition member 36 is configured to partition first chamber S1 into a first region on the flow inlet portion 31a side and a second region on the flow outlet portion 31b side. That is to say, partition member 36 is disposed between flow inlet portion 31a and flow outlet portion 31b in flow path 33 extending from flow inlet portion 31a to flow outlet portion 31b.
  • Valve portion 34 has a valve body 34a and a valve seat 34b. Valve portion 34 is configured to adjust the degree of opening by the gap between valve body 34a and valve seat 34b. Valve body 34a is formed in a shaft shape. One end (first end) of valve body 34a is connected to diaphragm 32. The other end (second end) of valve body 34a is connected to spring 35. Valve body 34a is configured to move in the direction indicated by a double-pointed arrow A3 in Fig. 2 due to the deformation of diaphragm 32. That is to say, valve body 34a is configured to move in the axial direction of valve body 34a due to the deformation of diaphragm 32.
  • Valve body 34a has a tapered shape with a cross-section continuously decreasing from the one end to the other end. Valve body 34a is formed in a truncated cone shape and is formed with a diameter continuously decreasing in the axial direction toward valve seat 34b.
  • Valve seat 34b is provided in partition member 36. Valve seat 34b is disposed between flow inlet portion 31a and flow outlet portion 31b in flow path 33 extending from flow inlet portion 31a to flow outlet portion 31b. Valve seat 34b is provided around a valve hole 37 passing through valve seat 34b. Valve body 34a moves in the axial direction of valve body 34a due to the deformation of diaphragm 32 and accordingly leaves valve seat 34b, thereby opening valve hole 37. Specifically, when the pressure of the refrigerant in flow path 33 exceeds the pressure of the inert gas in pressure reference chamber S2, diaphragm 32 curves in a projecting manner toward pressure reference chamber S2.
  • valve body 34a connected to diaphragm 32 to move toward pressure reference chamber S2 in the axial direction of valve body 34a.
  • the other end of valve body 34a accordingly leaves valve seat 34b to expose valve hole 37 from valve body 34a, thereby opening valve hole 37.
  • Valve seat 34b is configured such that each of the surface (upper surface) on the first region side of first chamber S1 and the surface (lower surface) on the second region side of first chamber S1 becomes dented. That is to say, valve seat 34b has a dent on each of the first region side and the second region side of first chamber S1. In valve seat 34b, the bottom of the dent on the first region side of first chamber S1 and the bottom of the dent on the second region side of first chamber S1 are communicated with each other. The bottom of the dent on the first region side of first chamber S1 and the bottom of the dent on the second region side of first chamber S1 which are communicated with each other define valve hole 37.
  • valve seat 34b is formed such that each of the surface on the first region side of first chamber S1 and the surface on the second region side of first chamber S1 is formed in a cone shape.
  • Valve seat 34b is formed in a cone shape such that the surface on the first region side of first chamber S1 has a diameter continuously decreasing toward the second region of first chamber S1.
  • the surface of valve seat 34b on the first region side of first chamber S1 is formed in a cone shape to have a diameter continuously decreasing toward second region of first chamber S1.
  • Valve portion 34 is configured to increase the degree of opening when the pressure in flow path 33 is higher than the pressure in pressure reference chamber S1. That is to say, valve portion 34 is configured as follows. When the pressure in flow path 33 is higher than the pressure in pressure reference chamber S2, valve body 34a moves toward diaphragm 32 in the axial direction of valve body 34a to increase the gap between valve body 34a and valve seat 34b, thereby increasing the degree of opening. Valve portion 34 is also configured to reduce the degree of opening when the pressure in flow path 35 is lower than the pressure in pressure reference chamber S2. That is to say, valve portion 34 is configured as follows. When the pressure in flow path 35 is lower than the pressure in pressure reference chamber S2, valve body 34a moves toward spring 35 in the axial direction of valve body 34a to reduce the gap between valve body 34a and valve seat 34b, thereby reducing the degree of opening.
  • Valve portion 34 is configured to continuously change the size of the gap between valve body 34a and valve seat 34b by valve body 34a moving in the axial direction of valve body 34a due to the deformation of diaphragm 32. That is to say, valve portion 34 is configured to increase or reduce the degree of opening of valve portion 34 in proportional to the amount of movement in the axial direction of valve body 34a.
  • Spring 35 is connected to the other end of valve body 34a and the bottom of case 31. Spring 35 is configured to bias valve body 34a toward the bottom of case 31 by elastic force.
  • a small hole 38 is provided in partition member 36. Small hole 38 is provided to pass through partition member 36. Small hole 38 defines a part of flow path 33. Since small hole 38 is not closed by valve body 34a and is open constantly, refrigerant can constantly flow through small hole 38 from the first region to the second region in first chamber S1. In the present embodiment, small hole 38 has the function as a capillary. That is to say, the refrigerant is decompressed by flowing through small hole 38.
  • the refrigerant that has flowed into compressor 1 is compressed by compressor 1 to turn into high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from compressor 1 flows through pipe PI1 into condenser 2.
  • the refrigerant that has flowed into condenser 2 is subjected to heat exchange with the air in condenser 2.
  • the refrigerant is condensed by heat dissipation to the air, and the air is heated by the refrigerant.
  • High-pressure liquid refrigerant condensed by condenser 2 flows through pipe PI2 into pressure-regulating valve 3.
  • the refrigerant that has flowed into pressure-regulating valve 3 is decompressed by pressure-regulating valve 3 to turn into low-pressure gas-liquid two-phase refrigerant.
  • the refrigerant decompressed by pressure-regulating valve 3 flows through pipe PI3 into evaporator 4.
  • the refrigerant that has flowed into evaporator 4 is subjected to heat exchange with the air in evaporator 4. Specifically, in evaporator 4, the air is cooled by the refrigerant, and the refrigerant turns into low-pressure gas refrigerant.
  • the refrigerant decompressed by evaporator 4 to turn into low-pressure gas flows through pipe PI4 into compressor 1.
  • the refrigerant flowing into compressor 1 is compressed and pressurized again and subsequently discharged from compressor 1.
  • valve body 34a is in contact with valve seat 34b. This maintains the state in which valve hole 37 is closed by valve body 34a. Valve portion 34 is closed in this state.
  • valve body 34a moves toward pressure reference chamber S2 in the axial direction of valve body 34a due to the deformation of diaphragm 32, the gap between valve body 34a and valve seat 34b increases. That is to say, the degree of opening of valve portion 34 increases.
  • valve body 34a The amount of movement in the axial direction of valve body 34a can be adjusted by the pressure of the refrigerant in flow path 33, the pressure of the inert gas in pressure reference chamber S2, and the biasing force of spring 35 connected to valve body 34a.
  • the degree of opening of valve portion 34 can be adjusted by the gap between valve body 34a and valve seat 34b.
  • the amount of the refrigerant flowing through pressure-regulating valve 3 can thus be adjusted by adjusting the amount of movement in the axial direction of valve body 34a and the degree of opening of valve portion 34.
  • air conditioner 10 of the comparative example differs from air conditioner 10 of the present embodiment in that it includes a linear expansion valve (LEV) 30, a thermistor 7, and a microcomputer 8.
  • microcomputer 8 controls the degree of opening of LEV 30 based on a signal from thermistor 7 that has detected the temperature of the refrigerant discharged from compressor 1, so that the temperature of the refrigerant discharged from compressor 1 is adjusted not to exceed a set temperature (a temperature set to prevent a failure of compressor 1).
  • refrigerant is R32.
  • R32 is refrigerant which has a small politropic exponent and whose temperature easily increases when discharged from compressor 1.
  • the temperature of the refrigerant discharged from compressor 1 increases easily at high outside air (high outside air temperature) and at high condensation temperature.
  • Air conditioner 10 of the present embodiment sets the pressure in pressure reference chamber S2 to the pressure in flow path 33 where the temperature of the refrigerant discharged from compressor 1 is the set temperature (the temperature set to prevent a failure of compressor 1), thereby increasing the degree of opening of valve portion 34 when the pressure in flow path 33 is higher than the pressure in pressure reference chamber S2. This can suppress the temperature of the refrigerant discharged from compressor 1 exceeding the set temperature.
  • the amount of the refrigerant flowing into evaporator 4 can also be increased by increasing the amount of the refrigerant flowing through pressure-regulating valve 3, thus reducing the degree of superheat. An increase in the temperature of the refrigerant discharged from compressor 1 can thus be suppressed.
  • the generation of hunting can be suppressed by adjusting the degree of opening of valve portion 34 before the temperature of the refrigerant discharged from compressor 1 exceeds the set temperature.
  • R32 is low GWP refrigerant. Consequently, air conditioner 10 that reduces refrigerant consumption with the use of low GWP refrigerant can be achieved.
  • Air conditioner 10 of the comparative example needs LEV 30, thermistor 7, and microcomputer 8 to adjust the temperature of the refrigerant discharged from compressor 1, leading to a complex configuration of air conditioner 10. Also, the cost of manufacturing air conditioner 10 is increased. Contrastingly, in air conditioner 10 of the present embodiment, pressure-regulating valve 3 can adjust the temperature of the refrigerant discharged from compressor 1, leading to a simple configuration of air conditioner 10. Also, the cost of manufacturing air conditioner 10 is reduced.
  • pressure-regulating valve 3 can adjust the flow rate of the refrigerant flowing through flow path 33 by adjusting the degree of opening of valve portion 34.
  • the generation of hunting can be suppressed more than in the case where valve portion 34 is merely opened/closed (ON/OFF).
  • the controllability of the flow rate of refrigerant can be improved.
  • the amount of refrigerant flowing through refrigerant circuit 13 is 300 g or more and 500 g or less.
  • the average refrigerant chlorofluorocarbon (CFC) charge amount of a room air conditioner is 800 g.
  • Air conditioner 10 of the present embodiment can thus reduce the amount of refrigerant to about a half of 800 g that is the average refrigerant CFC charge amount of a room air conditioner. If the amount of refrigerant is 400 g ⁇ 100 g, where 400 g is a half of the average refrigerant CFC charge amount of a room air conditioner, the refrigerant consumption can be reduced while maintaining the cooling capacity.
  • air conditioner 10 of the comparative example a reduced amount of refrigerant results in a shorter response time of the temperature of the refrigerant discharged from compressor 1 with respect to the adjustment of the degree of opening of LEV 30, so hunting may occur at the set temperature.
  • air conditioner 10 of the present embodiment increases the degree of opening of valve portion 34 with reference to the pressure in pressure reference chamber S2, thereby suppressing the generation of hunting with respect to the set temperature even when the amount of refrigerant decreases. Controllability can thus be improved.
  • compressor 1 can variably control the number of rotations. Power consumption can thus be reduced by variably controlling the number of rotations of compressor 1. Also, even when the temperature of the refrigerant discharged from compressor 1 increases due to an increase in the number of rotations of compressor 1, an increase in the temperature of the refrigerant discharged from compressor 1 can be suppressed by increasing the degree of opening of valve portion 34 with reference to the pressure in pressure reference chamber S2.
  • Embodiment 2 The same components as those of Embodiment 1 will be denoted by the same reference signs in Embodiment 2, and description thereof will not be repeated, unless otherwise noted.
  • This embodiment is not an embodiment of the invention but helpful to understand certain aspects thereof.
  • air conditioner 10 of Embodiment 2 differs from air conditioner 10 of Embodiment 1 in the configuration of pressure-regulating valve 3.
  • pressure-regulating valve 3 additionally includes a capillary 39.
  • Capillary 39 is connected to case 31 of pressure-regulating valve 3 and evaporator 4.
  • the configuration in case 31 of pressure-regulating valve 3 is identical to the configuration of Embodiment 1.
  • Capillary 39 is disposed between valve portion 34 and evaporator 4 in refrigerant circuit 13. Capillary 39 can thus decompress the refrigerant.
  • the present embodiment can adjust the decompression of refrigerant by capillary 39. This leads to easier adjustment of the decompression of the refrigerant.
  • Embodiment 1 The same components as those of Embodiment 1 will be denoted by the same reference signs in Embodiment 3, and description thereof will not be repeated, unless otherwise noted.
  • This embodiment is not an embodiment of the invention but helpful to understand certain aspects thereof.
  • air conditioner 10 of Embodiment 3 differs from air conditioner 10 of Embodiment 1 in the configuration of pressure-regulating valve 3.
  • pressure-regulating valve 3 includes capillary 39.
  • Capillary 39 is connected in parallel with case 31 of pressure-regulating valve 3 in refrigerant circuit 13.
  • the configuration in case 31 of pressure-regulating valve 3 is identical to the configuration of Embodiment 1.
  • Capillary 39 is disposed in parallel with valve portion 34 in refrigerant circuit 13. Capillary 39 can thus decompress the refrigerant.
  • the present embodiment can accordingly adjust the decompression of refrigerant by capillary 39.
  • the adjustment of the decompression of refrigerant can thus be simplified.
  • Capillary 39 can adjust the decompression of refrigerant more easily than small hole 38 of Embodiment 1. In the modification of air conditioner 10 of the present embodiment, thus, capillary 39 can adjust the decompression of refrigerant easily.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Safety Valves (AREA)
  • Temperature-Responsive Valves (AREA)

Claims (5)

  1. Climatiseur (10) comprenant :
    un circuit de réfrigérant (13) comprenant un compresseur (1), un condenseur (2), une vanne de régulation de pression (3), et un évaporateur (4) ; et
    du réfrigérant s'écoulant à travers le circuit de réfrigérant (13) dans l'ordre du compresseur (1), du condenseur (2), de la vanne de régulation de pression (3), et de l'évaporateur (4), dans lequel
    le réfrigérant est le R32,
    la vanne de régulation de pression (3) comprend
    un carter (31),
    une membrane (32) attachée à un côté interne du carter (31) pour séparer un intérieur du carter (31),
    un trajet d'écoulement (33) fourni par séparation de l'intérieur du carter (31) par la membrane (32), le trajet d'écoulement (33) amenant le réfrigérant s'écoulant depuis le condenseur (2) à s'écouler jusqu'à l'évaporateur (4),
    une chambre de référence de pression (S2) séparée du chemin d'écoulement (33) par la membrane (32) et remplie de gaz inerte,
    une portion de vanne (34) disposée sur le trajet d'écoulement (33),
    un ressort (35) raccordé à un fond du carter (31), et
    un élément de séparation (36) disposé sur le trajet d'écoulement (33),
    la vanne de régulation de pression (3) est configurée pour ajuster un degré d'ouverture de la portion de vanne (34) pour ajuster un débit du réfrigérant s'écoulant à travers le trajet d'écoulement (33), et
    la portion de vanne (34) est configurée pour
    augmenter le degré d'ouverture lorsqu'une pression sur le trajet d'écoulement (33) est supérieure à une pression dans la chambre de référence de pression (S2), et
    réduire le degré d'ouverture lorsque la pression sur le trajet d'écoulement (33) est inférieure à la pression dans la chambre de référence de pression (S2),
    la portion de vanne (34) comprend
    un corps de vanne (34a) raccordé à la membrane (32), et
    un siège de vanne (34b) prévu dans l'élément de séparation (36), et
    une première extrémité du corps de vanne (34a) est raccordée à la membrane (32) et une seconde extrémité du corps de vanne (34a) est raccordée au ressort (35),
    le ressort (35) est configuré pour solliciter le corps de vanne (34a) vers le fond du carter (31) par une force élastique,
    la portion de vanne (34) est configurée pour
    lorsque la pression sur le trajet d'écoulement (33) est supérieure à la pression dans la chambre de référence de pression (S2), le corps de vanne (34a) se déplace vers la membrane (32) dans la direction axiale du corps de vanne (34a) pour augmenter un écartement entre le corps de vanne (34a) et le siège de vanne (34b), et ainsi augmenter le degré d'ouverture, et
    lorsque la pression sur le chemin d'écoulement (33) est inférieure à la pression dans la chambre de référence de pression (S2), le corps de vanne (34a) se déplace vers le ressort (35) dans la direction axiale du corps de vanne (34a) pour réduire l'écartement entre le corps de vanne (34a) et le siège de vanne (34b), et ainsi réduire le degré d'ouverture,
    un petit trou (38) est prévu dans l'élément de séparation (36), et
    la vanne de régulation de pression (3) est configurée pour amener le réfrigérant à s'écouler dans la vanne de régulation de pression (3) à travers le petit trou (38) également lorsque le corps de vanne (34a) est en contact avec le siège de vanne (34b).
  2. Climatiseur (10) selon la revendication 1, dans lequel, pendant le fonctionnement du climatiseur (1), une quantité de réfrigérant s'écoulant dans le circuit de réfrigérant (13) est de 300 g ou plus et de 500 g ou moins.
  3. Climatiseur (10) selon la revendication 1 ou 2, dans lequel
    la vanne de régulation de pression (3) comprend un capillaire (39), et
    le capillaire (39) est disposé entre la portion de vanne (34) et l'évaporateur (4) dans le circuit de réfrigérant (13).
  4. Climatiseur selon la revendication 1 ou 2, dans lequel
    la vanne de régulation de pression (3) comprend un capillaire (39), et
    le capillaire (39) est disposé en parallèle avec la portion de vanne (34) dans le circuit de réfrigérant (13).
  5. Climatiseur (10) selon l'une quelconque des revendications 1 à 4, dans lequel
    le compresseur (1) est configuré pour commander de manière variable un nombre de rotations.
EP16920284.3A 2016-10-28 2016-10-28 Climatiseur Active EP3534088B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2016/082119 WO2018078808A1 (fr) 2016-10-28 2016-10-28 Climatiseur

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EP3534088A1 EP3534088A1 (fr) 2019-09-04
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EP3534088B1 true EP3534088B1 (fr) 2022-03-02

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WO2018078808A1 (fr) 2018-05-03
KR20190032560A (ko) 2019-03-27
AU2016427727B2 (en) 2019-10-10
US20210172659A1 (en) 2021-06-10
US20210180842A1 (en) 2021-06-17
CN109891164A (zh) 2019-06-14
EP3534088A1 (fr) 2019-09-04
EP3534088A4 (fr) 2019-10-30
KR102147693B1 (ko) 2020-08-25
US20200018530A1 (en) 2020-01-16
AU2016427727A1 (en) 2019-02-21
JP6312943B1 (ja) 2018-04-18
JPWO2018078808A1 (ja) 2018-11-01

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