US20230099489A1 - Refrigeration cycle apparatus - Google Patents

Refrigeration cycle apparatus Download PDF

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Publication number
US20230099489A1
US20230099489A1 US17/800,331 US202017800331A US2023099489A1 US 20230099489 A1 US20230099489 A1 US 20230099489A1 US 202017800331 A US202017800331 A US 202017800331A US 2023099489 A1 US2023099489 A1 US 2023099489A1
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United States
Prior art keywords
way valve
heat exchanger
state
connecting pipe
aperture
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US17/800,331
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English (en)
Inventor
Shunya GYOTOKU
Satoru Yanachi
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YANACHI, SATORU, GYOTOKU, Shunya
Publication of US20230099489A1 publication Critical patent/US20230099489A1/en
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    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02732—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two three-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

Definitions

  • the present disclosure relates to a refrigeration cycle apparatus.
  • a refrigeration cycle apparatus including an outdoor unit, a plurality of indoor units, and a branch unit, wherein the outdoor unit and the plurality of indoor units are connected via the branch unit.
  • Japanese Patent Laying-Open No. 4-6361 discloses a refrigeration cycle apparatus in which an outdoor unit and a branch unit are connected via a first refrigerant pipe and a second refrigerant pipe.
  • the refrigeration cycle apparatus includes: a first refrigerant flow path switching mechanism arranged in the outdoor unit; and a second refrigerant flow path switching mechanism arranged in the branch unit.
  • the first flow path switching mechanism includes one four-way valve and four check valves.
  • the first refrigerant flow path mechanism switches between a cooling operation state in which the outdoor heat exchanger acts as a condenser and a heating operation state in which the outdoor heat exchanger acts as an evaporator, and a state in which the pressure of the refrigerant flowing through the first refrigerant pipe is lower than the pressure of the refrigerant flowing through the second refrigerant pipe is maintained irrespective of the switching between the cooling operation state and the heating operation state.
  • the inner diameter of the first refrigerant pipe is larger than the inner diameter of the second refrigerant pipe.
  • the second flow path switching mechanism includes a plurality of flow path switching valves.
  • the second refrigerant flow path mechanism switches between a full-cooling operation state or full-heating operation state in which all of the plurality of indoor units each act as an evaporator or condenser and a cooling-dominated operation state or heating-dominated operation in which part of the plurality of indoor units each act as a condenser and the other part of the plurality of indoor units each act as an evaporator.
  • a refrigeration cycle apparatus comprises a refrigerant circuit in which refrigerant circulates, the refrigerant circuit comprising a compressor, a flow path switching portion, an outdoor heat exchanger, a decompressing apparatus, a first indoor heat exchanger, a first connecting pipe through which the refrigerant flows into the first indoor heat exchanger, and a second connecting pipe through which the refrigerant flows from the first indoor heat exchanger.
  • the flow path switching portion is configured to switch between a cooling operation state in which the outdoor heat exchanger acts as a condenser and a heating operation state in which the outdoor heat exchanger acts as an evaporator.
  • the refrigerant circuit further comprises: a first three-way valve arranged downstream of the first indoor heat exchanger in the cooling operation state and arranged upstream of the first indoor heat exchanger in the heating operation state; and a second three-way valve arranged upstream of the first indoor heat exchanger in the cooling operation state and arranged downstream of the first indoor heat exchanger in the heating operation state.
  • Each of the first three-way valve and the second three-way valve comprises: a valve seat having a valve chamber and provided with a first aperture, a second aperture and a third aperture, the first aperture, the second aperture, and the third aperture being connected to the valve chamber; and a valve body configured to move among a first position, a second position, and a third position in the valve chamber.
  • the first aperture of each of the first three-way valve and the second three-way valve is connected to one end or the other end of the first indoor heat exchanger in the refrigerant circuit.
  • the second aperture of each of the first three-way valve and the second three-way valve is connected to the first connecting pipe.
  • the third aperture of each of the first three-way valve and the second three-way valve is connected to the second connecting pipe.
  • Each of the first three-way valve and the second three-way valve is configured to be switched independently to one of a first state in which the valve body is located at the first position, a second state in which the valve body is located at the second position, and a third state in which the valve body is located at the third position.
  • a first space is arranged in the valve chamber, the first space communicating with the first aperture and the second aperture and being separated from the third aperture
  • a second space is arranged in the valve chamber, the second space communicating with the first aperture, the second aperture, and the third aperture
  • a third space is arranged in the valve chamber, the third space communicating with the first aperture and the third aperture and being separated from the second aperture.
  • a refrigeration cycle apparatus can be provided to suppress occurrence of chattering while preventing decreased comfortability when load of an indoor heat exchanger is decreased.
  • FIG. 1 is a diagram showing a refrigerant circuit of a refrigeration cycle apparatus according to the present embodiment.
  • FIG. 2 is a cross sectional view showing a valve seat, a valve chamber, and a valve body when a first three-way valve according to the present embodiment is in a first state.
  • FIG. 3 is a cross sectional view when viewed from an arrow shown in FIG. 2 .
  • FIG. 4 is a cross sectional view showing the valve seat, the valve chamber, and the valve body when the first three-way valve according to the present embodiment is in a second state.
  • FIG. 5 is a cross sectional view when viewed from an arrow V-V shown in FIG. 4 .
  • FIG. 6 is a cross sectional view showing the valve seat, the valve chamber, and the valve body when the first three-way valve according to the present embodiment is in a third state.
  • FIG. 7 is a cross sectional view when viewed from an arrow VII-VII shown in FIG. 6 .
  • FIG. 8 is a diagram showing the refrigerant circuit when the refrigeration cycle apparatus according to the present embodiment is in a full-cooling operation state.
  • FIG. 9 is a diagram showing the refrigerant circuit when load of a first indoor heat exchanger is decreased to be lower than that in the state shown in FIG. 8 when the refrigeration cycle apparatus according to the present embodiment is in a full-cooling operation state.
  • FIG. 10 is a diagram showing the refrigerant circuit when the refrigeration cycle apparatus according to the present embodiment is in a full-heating operation state.
  • FIG. 11 is a diagram showing the refrigerant circuit when the load of the first indoor heat exchanger is decreased to be lower than that in the state shown in FIG. 10 when the refrigeration cycle apparatus according to the present embodiment is in the full-heating operation state.
  • FIG. 12 is a diagram showing the refrigerant circuit when the refrigeration cycle apparatus according to the present embodiment is in a first cooling-dominated operation state.
  • FIG. 13 is a diagram showing the refrigerant circuit when the refrigeration cycle apparatus according to the present embodiment is in a first heating-dominated operation state.
  • FIG. 14 is a cross sectional view showing a valve seat, a valve chamber, and a valve body when a modification of the first three-way valve shown in FIG. 2 is in the first state.
  • FIG. 15 is a cross sectional view showing the valve seat, the valve chamber, and the valve body when the modification of the first three-way valve shown in FIG. 2 is in the second state.
  • FIG. 16 is a cross sectional view showing the valve seat, the valve chamber, and the valve body when the modification of the first three-way valve shown in FIG. 2 is in the third state.
  • a refrigeration cycle apparatus 1000 includes a refrigerant circuit in which refrigerant circulates.
  • the refrigerant circuit includes a compressor 1 , a four-way valve 2 serving as a flow path switching portion, an outdoor heat exchanger 3 , a first decompressing apparatus 4 A, a second decompressing apparatus 4 B, a first indoor heat exchanger 5 A, a second indoor heat exchanger 5 B, a first check valve 6 A, a second check valve 6 B, a third check valve 6 C, a fourth check valve 6 D, a gas-liquid separator 7 , a first three-way valve 8 A, a second three-way valve 9 A, a third three-way valve 8 B, a fourth three-way valve 9 B, a first connecting pipe 10 , a second connecting pipe 11 , a third connecting pipe 12 A, a fourth connecting pipe 13 A, a fifth connecting pipe 12 B, and a sixth connecting pipe 13 B.
  • Compressor 1 four-way valve 2 , outdoor heat exchanger 3 , first check valve 6 A, second check valve 6 B, third check valve 6 C, and fourth check valve 6 D are accommodated in an outdoor unit 100 .
  • First decompressing apparatus 4 A and first indoor heat exchanger 5 A are accommodated in a first indoor unit 200 A.
  • Second decompressing apparatus 4 B and second indoor heat exchanger 5 B are accommodated in a second indoor unit 200 B.
  • Gas-liquid separator 7 , first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B are accommodated in a branch unit 300 .
  • First connecting pipe 10 and second connecting pipe 11 are arranged between outdoor unit 100 and branch unit 300 so as to connect outdoor unit 100 and branch unit 300 to each other.
  • Third connecting pipe 12 A and fourth connecting pipe 13 A are arranged between first indoor unit 200 A and branch unit 300 so as to connect first indoor unit 200 A and branch unit 300 to each other.
  • Fifth connecting pipe 12 B and sixth connecting pipe 13 B are arranged between second indoor unit 200 B and branch unit 300 so as to connect second indoor unit 200 B and branch unit 300 to each other.
  • Compressor 1 has a discharge port through which the refrigerant is discharged and a suction port through which the refrigerant is suctioned.
  • Compressor 1 is, for example, a constant-speed compressor having a constant driving frequency. It should be noted that compressor 1 may be, for example, an inverter compressor having a driving frequency controlled by an inverter.
  • Four-way valve 2 has first to fourth ports.
  • the first port is connected to the discharge port of compressor 1 .
  • the second port is connected to the suction port of compressor 1 .
  • the third port is connected to first connecting pipe 10 via outdoor heat exchanger 3 and first check valve 6 A, and is connected to second connecting pipe 11 via outdoor heat exchanger 3 and second check valve 6 B.
  • the fourth port is connected to first connecting pipe 10 via third check valve 6 C, and is connected to second connecting pipe 11 via fourth check valve 6 D.
  • Four-way valve 2 switches between a cooling operation state in which the first port communicates with the third port and the second port communicates with the fourth port and a heating operation state in which the first port communicates with the fourth port and the second port communicates with the third port.
  • First decompressing apparatus 4 A and second decompressing apparatus 4 B are, for example, expansion valves. In each of first decompressing apparatus 4 A and second decompressing apparatus 4 B, the refrigerant is expanded. In each of first indoor heat exchanger 5 A and second indoor heat exchanger 5 B, heat is exchanged between the refrigerant circulating in the refrigerant circuit and indoor air.
  • First indoor unit 200 A and second indoor unit 200 B are installed, for example, in different rooms.
  • Outdoor unit 100 is provided with: a refrigerant flow path that connects between outdoor heat exchanger 3 and first connecting pipe 10 ; a refrigerant flow path that connects between outdoor heat exchanger 3 and second connecting pipe 11 ; a refrigerant flow path that connects between the fourth port of four-way valve 2 and first connecting pipe 10 ; and a refrigerant flow path that connects between the fourth port of four-way valve 2 and second connecting pipe 11 .
  • First check valve 6 A is arranged in the refrigerant flow path between outdoor heat exchanger 3 and first connecting pipe 10 , and permits only the flow of the refrigerant from outdoor heat exchanger 3 to first connecting pipe 10 .
  • First check valve 6 A blocks the flow of the refrigerant from first connecting pipe 10 to outdoor heat exchanger 3 .
  • Second check valve 6 B is arranged in the refrigerant flow path between outdoor heat exchanger 3 and second connecting pipe 11 , and permits only the flow of the refrigerant from second connecting pipe 11 to the outdoor heat exchanger. Second check valve 6 B blocks the flow of the refrigerant from second connecting pipe 11 to outdoor heat exchanger 3 .
  • Third check valve 6 C is arranged in the refrigerant flow path between the fourth port of four-way valve 2 and first connecting pipe 10 , and permits only the flow of the refrigerant from the fourth port of four-way valve 2 to the second connecting pipe. Third check valve 6 C blocks the flow of the refrigerant from first connecting pipe 10 to the fourth port of four-way valve 2 .
  • Fourth check valve 6 D is arranged in the refrigerant flow path between the fourth port of four-way valve 2 and second connecting pipe 11 , and peimits only the flow of the refrigerant from second connecting pipe 11 to the fourth port of four-way valve 2 .
  • Fourth check valve 6 D blocks the flow of the refrigerant from the fourth port of four-way valve 2 to second connecting pipe 11 .
  • Gas-liquid separator 7 is connected to first connecting pipe 10 and has an flow inlet 71 via which the refrigerant flows in, a first flow outlet 72 via which the gas-phase refrigerant flows out, and a second flow outlet 73 via which the liquid-phase refrigerant flows out.
  • First three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B have the same configuration. As shown in FIGS. 2 to 7 , each of first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B includes a valve seat 14 and a valve body 15 .
  • Each of valve seats 14 of first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B includes a valve chamber 16 and is provided with a first aperture Pl, a second aperture P 2 , and a third aperture P 3 , first aperture P 1 , second aperture P 2 , and third aperture P 3 communicating with valve chamber 16 .
  • Valve seat 14 has a first surface 14 A facing valve chamber 16 and provided with one end of each of first aperture P 1 and third aperture P 3 , and a second surface 14 B provided with one end of second aperture P 2 .
  • First aperture P 1 is arranged beside third apertures P 3 with an interval being interposed therebetween in a peripheral direction serving as a first direction.
  • the aperture area of third aperture P 3 is equal to, for example, the aperture area of first aperture P 1 .
  • Second surface 14 B faces first surface 14 A with valve body 15 being interposed therebetween in a Z direction serving as a second direction, for example.
  • Second aperture P 2 is arranged to overlap with the rotation axis of valve body 15 when viewed in the Z direction, for example.
  • the shortest distance between the respective centers of second aperture P 2 and first aperture P 1 is equal to, for example, the shortest distance between the respective centers of second aperture P 2 and third aperture P 3 .
  • First aperture P 1 of first three-way valve 8 A is connected to first indoor heat exchanger 5 A via third connecting pipe 12 A.
  • Second aperture P 2 of first three-way valve 8 A is connected to first flow outlet 72 of gas-liquid separator 7 . That is, second aperture P 2 of first three-way valve 8 A is connected to first connecting pipe 10 via gas-liquid separator 7 .
  • Third aperture P 3 of first three-way valve 8 A is connected to second connecting pipe 11 .
  • First aperture P I of second three-way valve 9 A is connected to first indoor heat exchanger 5 A via fourth connecting pipe 13 A.
  • Second aperture P 2 of second three-way valve 9 A is connected to second flow outlet 73 of gas-liquid separator 7 . That is, second aperture P 2 of second three-way valve 9 A is connected to first connecting pipe 10 via gas-liquid separator 7 .
  • Third aperture P 3 of second three-way valve 9 A is connected to second connecting pipe 11 .
  • First aperture P 1 of third three-way valve 8 B is connected to second indoor heat exchanger 5 B via fifth connecting pipe 12 B.
  • Second aperture P 2 of third three-way valve 8 B is connected to first flow outlet 72 of gas-liquid separator 7 . That is, second aperture P 2 of third three-way valve 8 B is connected to first connecting pipe 10 via gas-liquid separator 7 .
  • Third aperture P 3 of third three-way valve 8 B is connected to second connecting pipe 11 .
  • First aperture P 1 of fourth three-way valve 9 B is connected to second indoor heat exchanger 5 B via sixth connecting pipe 13 B.
  • Second aperture P 2 of fourth three-way valve 9 B is connected to second flow outlet 73 of gas-liquid separator 7 . That is, second aperture P 2 of fourth three-way valve 9 B is connected to first connecting pipe 10 via gas-liquid separator 7 .
  • Third aperture P 3 of fourth three-way valve 9 B is connected to second connecting pipe 11 .
  • Second aperture P 2 of first three-way valve 8 A and second aperture P 2 of third three-way valve 8 B are connected to first flow outlet 72 of gas-liquid separator 7 and first connecting pipe 10 in parallel with each other.
  • Third aperture P 3 of first three-way valve 8 A and third aperture P 3 of third three-way valve 8 B are connected to second connecting pipe 11 in parallel with each other.
  • Second aperture P 2 of second three-way valve 9 A and second aperture P 2 of fourth three-way valve 9 B are connected to second flow outlet 73 of gas-liquid separator 7 and first connecting pipe 10 in parallel with each other.
  • Third aperture P 3 of second three-way valve 9 A and third aperture P 3 of fourth three-way valve 9 B are connected to second connecting pipe 11 in parallel with each other.
  • valve bodies 15 of first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B moves among a first position, a second position, and a third position in valve chamber 16 .
  • Valve body 15 is provided to rotate about, for example, a rotation axis extending along the Z direction. Valve body 15 rotates, for example, in a peripheral direction from third aperture P 3 toward first aperture P 1 and in a direction opposite thereto. Valve body 15 is connected to a rotation shaft of a motor (not shown) via, for example, a gear 17 .
  • Valve body 15 has a third surface 18 slidable on first surface 14 A, and is provided with a recess 19 arranged beside third surface 18 in the peripheral direction serving as the first direction and recessed with respect to third surface 18 , and has a fourth surface 20 located opposite to third surface 18 and facing second surface 14 B of valve seat 14 with an interval being interposed therebetween in the Z direction.
  • Valve body 15 has: a first end portion 151 in the peripheral direction; and a second end portion 152 located opposite to first end portion 151 in the peripheral direction.
  • First end portion 151 is an end portion arranged on the front side with respect to second end portion 152 when valve body 15 rotates in the peripheral direction from third aperture P 3 toward first aperture P 1 .
  • Second end portion 152 is an end portion arranged on the front side with respect to first end portion 151 when valve body 15 rotates in the peripheral direction from first aperture P 1 toward third aperture P 3 .
  • Recess 19 has: a third end portion 191 in the peripheral direction; and a fourth end portion 192 located opposite to third end portion 191 in the peripheral direction.
  • Third end portion 191 is an end portion arranged on the rear side with respect to first end portion 151 and on the front side with respect to fourth end portion 192 when valve body 15 rotates in the peripheral direction from third aperture P 3 toward first aperture P 1 .
  • Fourth end portion 192 is an end portion arranged on the rear side with respect to second end portion 152 and on the front side with respect to third end portion 191 when valve body 15 rotates in the peripheral direction from first aperture P 1 toward third aperture P 3 .
  • An interval between first end portion 151 and third end portion 191 in the peripheral direction is wider than an interval between second end portion 152 and fourth end portion 192 in the peripheral direction.
  • Third surface 18 is arranged at least between first end portion 151 and third end portion 191 and around the entire periphery of recess 19 in the peripheral direction.
  • valve body 15 when valve body 15 is located at the second position, valve body 15 is provided not to overlap with at least a portion of each of first aperture P 1 and third aperture P 3 when viewed from the second aperture P 2 side. As indicated by a dotted line in FIG. 4 , when valve body 15 is located at the second position, valve body 15 is provided not to overlap with, for example, first aperture P 1 and third aperture P 3 when viewed from the second aperture P 2 side. Valve body 15 is provided to allow second space S 2 to be continuous to a whole of each of first aperture P 1 and third aperture P 3 .
  • an angle 01 formed with respect to the rotation axis by first end portion 151 and second end portion 152 of valve body 15 outside valve body 15 is equal to, for example, an angle ⁇ 2 formed with respect to the rotation axis by a first imaginary line L 1 passing through the rotation axis of valve body 15 and tangent to first aperture P 1 and a second imaginary line L 2 passing through the rotation axis of valve body 15 and tangent to third aperture P 3 .
  • recess 19 when viewed from the second aperture P 2 side, recess 19 is provided to overlap with a whole of each of first aperture P 1 and third aperture P 3 when valve body 15 is located at the third position.
  • An angle ⁇ 3 formed with respect to the rotation axis by third end portion 191 and fourth end portion 192 of recess 19 is equal to, for example, angle ⁇ 2 described above.
  • Each of first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B can be in the following three states: a first state in which valve body 15 is located at the first position; a second state in which valve body 15 is located at the second position; and a third state in which valve body 15 is located at the third position.
  • Each of first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B is switchable independently to one of the above-described three states.
  • valve body 15 in the first state, a first space S 1 communicating with first aperture P 1 and second aperture P 2 and separated from third aperture P 3 by valve body 15 is arranged in each valve chamber 16 .
  • valve body 15 does not overlap with first aperture P 1 in the Z direction.
  • Third surface 18 of valve body 15 overlaps with a whole of third aperture P 3 , and closes third aperture P 3 .
  • Recess 19 of valve body 15 does not overlap with first aperture PI and third aperture P 3 .
  • Third surface 18 is arranged to overlap with a whole of third aperture P 3 when viewed from the second aperture P 2 side.
  • First end portion 151 and third end portion 191 of valve body 15 are arranged to sandwich third aperture P 3 therebetween in the peripheral direction when viewed from the second aperture P 2 side.
  • Recess 19 is arranged not to overlap with first aperture P 1 and third aperture P 3 when viewed from the second aperture P 2 side.
  • valve body 15 does not overlap with first aperture P 1 in the Z direction.
  • Valve body 15 does not overlap with at least a portion of third aperture P 3 in the Z direction.
  • Valve body 15 is arranged, for example, at a second position indicated by a solid line in FIG. 4 .
  • third surface 18 is arranged to overlap with only a portion of third aperture P 3 when viewed from the second aperture P 2 side.
  • the aperture area of the region of third aperture P 3 which does not overlap with valve body 15 is smaller than the aperture area of first aperture P 1 , for example.
  • Valve body 15 may be arranged, for example, at the second position indicated by a dotted line in FIG. 4 .
  • third surface 18 is arranged not to overlap with third aperture P 3 when viewed from the second aperture P 2 side.
  • a third space S 3 communicating with first aperture P 1 and third aperture P 3 and separated from second aperture P 2 is arranged in recess 19 of valve body 15 .
  • recess 19 of valve body 15 is arranged to overlap with first aperture P 1 and third aperture P 3 in the Z direction.
  • Refrigeration cycle apparatus 1000 is switched by four-way valve 2 between a cooling operation state in which outdoor heat exchanger 3 acts as a condenser and a heating operation state in which outdoor heat exchanger 3 acts as an evaporator. Further, refrigeration cycle apparatus 1000 is switched by first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B to a full-cooling operation state, a cooling-dominated operation state, a full-heating operation state, or a heating-dominated operation.
  • refrigeration cycle apparatus 1000 In the full-cooling operation state, refrigeration cycle apparatus 1000 is switched among a first full-cooling operation state shown in FIG. 8 , a second full-cooling operation state shown in FIG. 9 , and a third full-cooling operation state not shown. Similarly, in the full-heating operation state, refrigeration cycle apparatus 1000 is switched among a first full-heating operation state shown in FIG. 10 , a second full-heating operation state shown in FIG. 11 , and a third full-heating operation state not shown.
  • the first full-cooling operation state shown in FIG. 8 is realized when each of loads of first indoor heat exchanger 5 A and second indoor heat exchanger 5 B is comparatively high.
  • each of first three-way valve 8 A and third three-way valve 8 B is in the third state
  • each of second three-way valve 9 A and fourth three-way valve 9 B is in the first state.
  • the refrigerant flows in the refrigerant circuit along arrows in FIG. 8 .
  • High-pressure gas-phase refrigerant discharged from compressor 1 is condensed in outdoor heat exchanger 3 into high-pressure liquid-phase refrigerant or gas-liquid two-phase refrigerant, and flows out to first connecting pipe 10 .
  • the high-pressure liquid-phase refrigerant or gas-liquid two-phase refrigerant having flowed through first connecting pipe 10 flows into gas-liquid separator 7 via flow inlet 71 .
  • the high-pressure liquid-phase refrigerant having flowed out from second flow outlet 73 is branched in branch unit 300 , reaches each of second apertures P 2 of second three-way valve 9 A and fourth three-way valve 9 B that are in the first state, flows through each of the first spaces, and flows out from each of first apertures P 1 to fourth connecting pipe 13 A or sixth connecting pipe 13 B.
  • the liquid-phase refrigerant having flowed through fourth connecting pipe 13 A is decompressed by first decompressing apparatus 4 A, is then evaporated in first indoor heat exchanger 5 A, and flows out to third connecting pipe 12 A as low-pressure gas-phase refrigerant.
  • the liquid-phase refrigerant having flowed through sixth connecting pipe 13 B is decompressed by second decompressing apparatus 4 B, is then evaporated in second indoor heat exchanger 5 B, and flows out to fifth connecting pipe 12 B as low-pressure gas-phase refrigerant.
  • the low-pressure gas-phase refrigerant having flowed through third connecting pipe 12 A or fifth connecting pipe 12 B reaches first apertures P 1 of first three-way valve 8 A and third three-way valve 8 B that are in the third state, flows through each of the third spaces, and then flows out from third apertures P 3 .
  • the flows of the gas-phase refrigerant from third apertures P 3 are merged in branch unit 300 and the gas-phase refrigerant flows out to second connecting pipe 11 .
  • the refrigerant discharged from compressor 1 flows through one of first indoor heat exchanger 5 A and second indoor heat exchanger 5 B, and is then suctioned into compressor 1 .
  • the second full-cooling operation state shown in FIG. 9 is realized when only the load of first indoor heat exchanger 5 A becomes lower than a predetermined value, for example. It should be noted that the load of second indoor heat exchanger 5 B in the second full-cooling operation state may be decreased to be lower than the load of second indoor heat exchanger 5 B in the first full-cooling operation state.
  • each of first three-way valve 8 A and third three-way valve 8 B is in the third state
  • fourth three-way valve 9 B is in the first state
  • second three-way valve 9 A is in the second state. That is, the second full-cooling operation state shown in FIG. 9 is different from the first full-cooling operation state shown in FIG. 8 only in that second three-way valve 9 A is in the second state.
  • the refrigerant flows in the refrigerant circuit along arrows in FIG. 9 .
  • the high-pressure liquid-phase refrigerant having flowed out from second flow outlet 73 is branched in branch unit 300 , and part of the high-pressure liquid-phase refrigerant reaches second aperture P 2 of second three-way valve 9 A that is in the second state.
  • the high-pressure liquid-phase refrigerant having flowed into second aperture P 2 of second three-way valve 9 A flows through the second space and is accordingly further branched in valve chamber 16 .
  • the part of the high-pressure liquid-phase refrigerant having flowed into second aperture P 2 of second three-way valve 9 A flows out from third aperture P 3 .
  • the liquid-phase refrigerant having flowed out from third aperture P 3 of second three-way valve 9 A is merged with the low-pressure gas-phase refrigerant having flowed out from each of third apertures P 3 of first three-way valve 8 A and third three-way valve 8 B in branch unit 300 , and flows out to second connecting pipe 11 .
  • the remainder of the high-pressure liquid-phase refrigerant having flowed into second aperture P 2 flows out from first aperture P 1 to fourth connecting pipe 13 A, is decompressed by first decompressing apparatus 4 A, and is then evaporated in first indoor heat exchanger 5 A.
  • an amount of refrigerant flowing through first indoor heat exchanger 5 A is controlled as a ratio of the aperture areas of first aperture P 1 and third aperture P 3 when viewed from the second aperture P 2 side of second three-way valve 9 A.
  • the ratio is controlled as a rotation angle of valve body 15 of second three-way valve 9 A.
  • the switching between the first full-cooling operation state shown in FIG. 8 and the second full-cooling operation state shown in FIG. 9 and the control of the rotation angle of valve body 15 of second three-way valve 9 A in the second full-cooling operation state shown in FIG. 9 are performed to bring the evaporation temperature in first indoor heat exchanger 5 A into a target evaporation temperature, for example.
  • valve body 15 of second three-way valve 9 A rotates from the first position to the second position.
  • the evaporation temperature is always or regularly measured by a temperature sensor (not shown) attached to first indoor heat exchanger 5 A, for example.
  • the determination of the evaporation temperature and the control of the rotation angle of valve body 15 are always or regularly performed by control unit 310 , for example.
  • the driving frequency of compressor 1 is constant, for example.
  • the expression “the driving frequency is constant” means that the maximum value and minimum value of the driving frequency fall within a range of 95% or more and 105% or less of the average value thereof.
  • the switching between the first full-cooling operation state shown in FIG. 8 and the second full-cooling operation state shown in FIG. 9 and the control of the rotation angle of valve body 15 of second three-way valve 9 A in the second full-cooling operation state shown in FIG. 9 may be performed when a difference between the evaporation temperature of first indoor heat exchanger 5 A and the target evaporation temperature falls out of a predetermined range.
  • the third full-cooling operation state is realized, for example, when only the load of second indoor heat exchanger 5 B becomes lower than a predetermined value.
  • each of first three-way valve 8 A and third three-way valve 8 B is in the third state
  • second three-way valve 9 A is in the first state
  • fourth three-way valve 9 B is in the second state.
  • the flow rate of the refrigerant flowing in second indoor heat exchanger 5 B in the third full-cooling operation state becomes lower than the flow rate of the refrigerant flowing in second indoor heat exchanger 5 B in the first full-cooling operation state shown in FIG. 8 .
  • the first full-heating operation state shown in FIG. 10 is realized when each of loads of first indoor heat exchanger 5 A and second indoor heat exchanger 5 B is comparatively high.
  • each of first three-way valve 8 A and third three-way valve 8 B is in the first state
  • each of second three-way valve 9 A and fourth three-way valve 9 B is in the third state.
  • the refrigerant flows in the refrigerant circuit along arrows in FIG. 10 .
  • High-pressure gas-phase refrigerant discharged from compressor 1 flows out to first connecting pipe 10 through third check valve 6 C.
  • the high-pressure gas-phase refrigerant having flowed through first connecting pipe 10 flows into gas-liquid separator 7 via flow inlet 71 .
  • the high-pressure gas-phase refrigerant having flowed out from first flow outlet 72 is branched in branch unit 300 , reaches each of second apertures P 2 of first three-way valve 8 A and third three-way valve 8 B that are in the first state, flows through each of the first spaces, and flows out from each of first apertures P 1 to third connecting pipe 12 A or fifth connecting pipe 12 B.
  • the gas-phase refrigerant having flowed through third connecting pipe 12 A is condensed in first indoor heat exchanger 5 A, is then decompressed by first decompressing apparatus 4 A, and flows out to fourth connecting pipe 13 A as low-pressure gas-liquid two-phase refrigerant.
  • the gas-phase refrigerant having flowed through fifth connecting pipe 12 B is condensed in second indoor heat exchanger 5 B, is then decompressed by second decompressing apparatus 4 B, and flows out to sixth connecting pipe 13 B as low-pressure gas-liquid two-phase refrigerant.
  • the flows of the gas-phase refrigerant from third apertures P 3 are merged in branch unit 300 and the gas-phase refrigerant flows out to second connecting pipe 11 .
  • the refrigerant discharged from compressor 1 flows through one of first indoor heat exchanger 5 A and second indoor heat exchanger 5 B, and is then suctioned into compressor 1 .
  • the second full-heating operation state shown in FIG. 11 is realized, for example, when only the load of first indoor heat exchanger 5 A becomes lower than a predetermined value. It should be noted that the load of second indoor heat exchanger 5 B in the second full-heating operation state shown in FIG. 11 may be decreased to be lower than that in the first full-heating operation state.
  • each of second three-way valve 9 A and fourth three-way valve 9 B is in the third state, third three-way valve 8 B is in the first state, and first three-way valve 8 A is in the second state. That is, the second full-heating operation state shown in FIG. 11 is different from the first full-heating operation state shown in FIG. 10 only in that first three-way valve 8 A is in the second state.
  • the refrigerant flows in the refrigerant circuit along arrows in FIG. 11 .
  • High-pressure gas-phase refrigerant having flowed out from first flow outlet 72 is branched in branch unit 300 , and part of the high-pressure gas-phase refrigerant reaches second aperture P 2 of first three-way valve 8 A that is in the second state.
  • the high-pressure gas-phase refrigerant having flowed into second aperture P 2 of first three-way valve 8 A flows through the second space and is accordingly further branched in valve chamber 16 .
  • Part of the high-pressure gas-phase refrigerant having flowed into second aperture P 2 of first three-way valve 8 A flows out from third aperture P 3 .
  • the gas-phase refrigerant having flowed out from third aperture P 3 of first three-way valve 8 A is merged with the low-pressure gas-phase refrigerant having flowed out from each of third apertures P 3 of second three-way valve 9 A and fourth three-way valve 9 B in branch unit 300 , and flows out to second connecting pipe 11 .
  • the remainder of the high-pressure gas-phase refrigerant having flowed into second aperture P 2 flows out from first aperture P 1 to third connecting pipe 12 A, and is condensed in first indoor heat exchanger 5 A.
  • an amount of refrigerant flowing through first indoor heat exchanger 5 A is controlled by first three-way valve 8 A.
  • the amount of refrigerant flowing through first indoor heat exchanger 5 A becomes smaller as the ratio of the aperture area of third aperture P 3 to the aperture area of first aperture P 1 of first three-way valve 8 A is higher.
  • the ratio is controlled as a rotation angle of valve body 15 of first three-way valve 8 A.
  • the switching between the first full-heating operation state shown in FIG. 10 and the second full-heating operation state shown in FIG. 11 , and the control of the rotation angle of valve body 15 of first three-way valve 8 A in the second full-heating operation state shown in FIG. 11 are performed to bring the condensation temperature in first indoor heat exchanger 5 A into a target condensation temperature, for example.
  • a target condensation temperature for example.
  • valve body 15 of first three-way valve 8 A rotates from the first position to the second position.
  • the condensation temperature is always or regularly measured by a temperature sensor (not shown) attached to first indoor heat exchanger 5 A, for example.
  • control unit 310 determines whether the condensation temperature and the control of the rotation angle of valve body 15 are always or regularly performed by control unit 310 , for example.
  • the driving frequency of compressor 1 is constant, for example.
  • the switching between the first full-heating operation state shown in FIG. 10 and the second full-heating operation state shown in FIG. 11 and the control of the rotation angle of valve body 15 of first three-way valve 8 A in the second full-heating operation state shown in FIG. 11 may be performed when a difference between the condensation temperature of first indoor heat exchanger 5 A and the target condensation temperature falls out of a predetermined range.
  • the third full-heating operation state is realized, for example, when only the load of second indoor heat exchanger 5 B becomes lower than a predetermined value.
  • each of second three-way valve 9 A and fourth three-way valve 9 B is in the third state
  • first three-way valve 8 A is in the first state
  • third three-way valve 8 B is in the second state.
  • the flow rate of the refrigerant flowing in second indoor heat exchanger 5 B in the third full-heating operation state becomes lower than the flow rate of the refrigerant flowing in second indoor heat exchanger 5 B in the first full-heating operation state shown in FIG. 10 .
  • the flow rate of the refrigerant flowing in the indoor heat exchanger in which the load is decreased can be decreased without decreasing the driving frequency of compressor 1 , thereby suppressing occurrence of chattering in first check valve 6 A, second check valve 6 B, third check valve 6 C, and fourth check valve 6 D while preventing decreased comfortability in the rooms in which the indoor units are arranged.
  • the switching among the full-cooling operation state, the cooling-dominated operation state, the full-heating operation state, and the heating-dominated operation state can be realized also when each of first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B is replaced with two or more electromagnetic valves (for example, eight electromagnetic valves).
  • the control unit needs to control movement of each of the valve bodies of the eight electromagnetic valves for the purpose of the switching.
  • the switching can be performed by controlling, by control unit 310 , only the movement of each of the valve bodies of the four three-way valves. Therefore, the number of ports of control unit 310 of refrigeration cycle apparatus 1000 is reduced as compared with that in the refrigeration cycle apparatus including the plurality of electromagnetic valves instead of the three-way valves.
  • valve body 15 may be arranged not to overlap with first aperture P 1 and third aperture P 3 when viewed from the second aperture P 2 side.
  • valve body 15 is arranged not to overlap with first aperture P 1 and third aperture P 3 when viewed from the second aperture P 2 side in the second state as indicated by a dotted line in FIG. 4
  • the flow rate of the refrigerant flowing through first indoor heat exchanger 5 A is further reduced as compared with the case where valve body 15 is arranged to overlap with part of third aperture P 3 when viewed from the second aperture P 2 side in the second state as indicated by a solid line in FIG. 4 .
  • Refrigeration cycle apparatus 1000 is switched between a first cooling-dominated operation state shown in FIG. 12 and a second cooling-dominated operation state (not shown) in the cooling-dominated operation state. Similarly, refrigeration cycle apparatus 1000 is switched between a first heating-dominated operation state shown in FIG. 13 and a second heating-dominated operation state (not shown) in the heating-dominated operation.
  • the first cooling-dominated operation state shown in FIG. 12 is realized when the load of first indoor heat exchanger 5 A acting as an evaporator is higher than the load of second indoor heat exchanger 5 B acting as a condenser.
  • each of first three-way valve 8 A and fourth three-way valve 9 B is in the third state
  • third three-way valve 8 B is in the first state
  • second three-way valve 9 A is in the second state.
  • the second cooling-dominated operation state is realized when the load of second indoor heat exchanger 5 B acting as an evaporator is higher than the load of first indoor heat exchanger 5 A acting as a condenser.
  • each of second three-way valve 9 A and third three-way valve 8 B is in the third state
  • first three-way valve 8 A is in the first state
  • fourth three-way valve 9 B is in the second state.
  • the first heating-dominated operation state shown in FIG. 13 is realized when the load of first indoor heat exchanger 5 A acting as a condenser is higher than the load of second indoor heat exchanger 5 B acting as an evaporator.
  • third three-way valve 8 B is in the third state
  • first three-way valve 8 A and fourth three-way valve 9 B are in the first state
  • second three-way valve 9 A is in the second state.
  • the second heating-dominated operation state is realized when the load of second indoor heat exchanger 5 B acting as a condenser is higher than the load of first indoor heat exchanger 5 A acting as an evaporator.
  • first three-way valve 8 A is in the third state
  • each of second three-way valve 9 A and third three-way valve 8 B is in the first state
  • fourth three-way valve 9 B is in the second state.
  • Refrigeration cycle apparatus 1000 may include three or more indoor heat exchangers and three-way valves twice as large as the number of the indoor heat exchangers.
  • refrigeration cycle apparatus 1000 may further include: a third indoor heat exchanger connected in parallel with first indoor heat exchanger 5 A and second indoor heat exchanger 5 B; a fifth three-way valve arranged downstream of the third indoor heat exchanger in the cooling operation state and arranged upstream of the third indoor heat exchanger in the heating operation state; and a sixth three-way valve arranged upstream of the third indoor heat exchanger in the cooling operation state and arranged downstream of the third indoor heat exchanger in the heating operation state.
  • the fifth three-way valve is connected in parallel with first three-way valve 8 A and third three-way valve 8 B.
  • the sixth three-way valve is connected in parallel with second three-way valve 9 A and fourth three-way valve 9 B.
  • first aperture P 1 may be arranged beside third aperture P 3 with an interval being interposed therebetween in the X direction serving as the first direction.
  • each of valve bodies 15 of first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B is provided to move back and forth along the X direction.
  • Third surface 18 of each valve body 15 is arranged beside recess 19 in the X direction. An interval between first end portion 151 and third end portion 191 in the X direction is larger than an interval between second end portion 152 and fourth end portion 192 in the X direction.
  • Fourth surface 20 of valve body 15 is provided to slide on second surface 14 B of valve seat 14 , for example.
  • Second aperture P 2 is arranged to face first aperture P 1 , for example.
  • fourth surface 20 of valve body 15 may be provided to face second surface 14 B of valve seat 14 with an interval being interposed therebetween, for example.
  • each of valve seats 14 is provided with a holding portion for holding a state in which first surface 14 A of valve seat 14 and third surface 18 of valve body 15 are in contact with each other.
  • each of first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B described above can also be in the three states, i.e., the first state, the second state, and the third state as with each of first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B shown in FIGS. 2 to 7 . Therefore, refrigeration cycle apparatus 1000 including first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B shown in FIGS. 14 to 16 can also exhibit the same effect as that of refrigeration cycle apparatus 1000 including first three-way valve 8 A, second three-way valve 9 A, third three-way valve 8 B, and fourth three-way valve 9 B shown in FIGS. 2 to 7 .
  • Refrigeration cycle apparatus 1000 may further include an apparatus configured to prevent liquid from returning to compressor 1 .
  • Examples of such an apparatus include an accumulator or a heat exchanger configured to exchange heat between the refrigerant discharged from compressor 1 and the refrigerant suctioned into compressor 1 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Multiple-Way Valves (AREA)
US17/800,331 2020-04-30 2020-04-30 Refrigeration cycle apparatus Pending US20230099489A1 (en)

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JPS5289738U (fr) * 1975-12-27 1977-07-05
JPH0754218B2 (ja) 1990-04-23 1995-06-07 三菱電機株式会社 空気調和装置
WO2009087733A1 (fr) * 2008-01-07 2009-07-16 Mitsubishi Electric Corporation Dispositif de cycle de réfrigération et vanne à quatre voies
JP2012037224A (ja) * 2010-07-13 2012-02-23 Daikin Industries Ltd 冷媒流路切換ユニット
JP2012036933A (ja) * 2010-08-04 2012-02-23 Daikin Industries Ltd 冷媒流路切換弁、及び空気調和装置
JP5988646B2 (ja) * 2012-03-28 2016-09-07 三菱電機株式会社 三方弁およびその三方弁を備えた空気調和装置
CN108291657B (zh) * 2015-11-20 2019-09-03 三菱电机株式会社 阀装置及空气调节装置
JP6893523B2 (ja) * 2016-09-30 2021-06-23 三菱電機株式会社 室内機
JP6605156B2 (ja) * 2016-11-15 2019-11-13 三菱電機株式会社 流路切替弁およびそれを用いた空気調和機
JP2018159507A (ja) * 2017-03-22 2018-10-11 大阪瓦斯株式会社 Ｇｈｐチラー
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JP7317224B2 (ja) 2023-07-28
WO2021220486A1 (fr) 2021-11-04

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