CN117203476A - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
CN117203476A
CN117203476A CN202180097177.6A CN202180097177A CN117203476A CN 117203476 A CN117203476 A CN 117203476A CN 202180097177 A CN202180097177 A CN 202180097177A CN 117203476 A CN117203476 A CN 117203476A
Authority
CN
China
Prior art keywords
heat exchanger
gas
refrigerant
flow path
outdoor
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.)
Pending
Application number
CN202180097177.6A
Other languages
Chinese (zh)
Inventor
松田拓也
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of CN117203476A publication Critical patent/CN117203476A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0313—Pressure sensors near the outdoor heat exchanger
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • 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
    • F25B2700/195—Pressures of the condenser
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21162—Temperatures of a condenser of the refrigerant at the inlet of the condenser
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser

Landscapes

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

Abstract

A flow path (R1) is provided in an air conditioner (1), and the flow path (R1) includes a portion connecting a gas distributor (23 a), a 2 nd portion (13 b), a 1 st portion (13 a), and a gas-liquid two-phase distributor (21 a) in this order. A flow path (R2) is provided, and the flow path (R2) includes a portion connecting the gas distributor (23 b), the 3 rd portion (15 a), the 4 th portion (15 b), and the gas-liquid two-phase distributor (21 b) in this order. The flow path (R1) and the flow path (R2) are connected in parallel to the refrigeration cycle (51) so as to connect the gas-liquid two-phase distributor (21 a) and the gas-liquid two-phase distributor (21 b) and to connect the gas distributor (23 a) and the gas distributor (23 b). The 1 st part (13 a) is disposed on the windward side, and the 2 nd part (13 b) is disposed on the leeward side. The 3 rd part (15 a) is disposed on the windward side, and the 4 th part (15 b) is disposed on the leeward side.

Description

Air conditioner
Technical Field
The present disclosure relates to air conditioners.
Background
As a refrigerant used in a refrigeration cycle apparatus such as an air conditioner, there is a non-azeotropic refrigerant mixture in which 2 or more kinds of refrigerants are mixed. Patent documents 1 and 2 exist as patent documents that disclose refrigeration cycle apparatuses using such non-azeotropic refrigerant mixtures.
In a heat exchanger of a refrigeration cycle apparatus using a non-azeotropic refrigerant mixture, in order to improve heat exchange efficiency between the refrigerant and air, the refrigerant is required to flow in a counter flow direction opposite to a ventilation direction of the air passing through the heat exchanger in the heat exchanger.
Accordingly, various proposals have been made to make the flow of the refrigerant flowing through the heat exchanger into a counter flow when the heat exchanger functions as both a condenser and an evaporator. In japanese patent application laid-open No. 08-170864 (patent document 1), an air conditioner using a six-way valve and an expansion valve is proposed. Further, japanese patent application laid-open No. 09-196489 (patent document 2) proposes an air conditioner using a bridge circuit using a check valve.
Prior art literature
Patent literature
Patent document 1: japanese patent laid-open No. 08-170864
Patent document 2: japanese patent laid-open No. 09-196489
Disclosure of Invention
Problems to be solved by the invention
In general, when the heat exchanger functions as an evaporator, a gas-liquid two-phase distributor is disposed on the inlet side of the refrigerant in the heat exchanger in order to distribute the refrigerant in the gas-liquid two-phase state of the gas refrigerant and the liquid refrigerant flowing into the heat exchanger. Inside the gas-liquid two-phase distributor, for example, an orifice (orifice) is disposed so as to uniformly distribute the refrigerant in the gas-liquid two-phase state.
On the other hand, when the heat exchanger functions as a condenser, a gas distributor having a relatively large volume is disposed on the inlet side of the refrigerant in the heat exchanger in order to suppress pressure loss of the gas refrigerant flowing into the heat exchanger.
In a heat exchanger using a general refrigerant, when the heat exchanger functions as a condenser and when the heat exchanger functions as an evaporator, the direction of flow of the refrigerant is reversed. Therefore, a gas-liquid two-phase distributor is disposed on one side of the heat exchanger, and a gas distributor is disposed on the other side.
In contrast, in the heat exchanger using the zeotropic refrigerant mixture, when the heat exchanger functions as a condenser and when the heat exchanger functions as an evaporator, the refrigerant flows in the same direction in the heat exchanger.
Therefore, when the heat exchanger functions as a condenser, for example, when the gas refrigerant flows through a gas-liquid two-phase distributor provided with a distributor (distributor), the pressure loss increases. In addition, when the heat exchanger functions as an evaporator, for example, when the gas refrigerant subjected to heat exchange flows through a gas-liquid two-phase distributor provided with a distributor (distributor), the pressure loss increases.
The present disclosure has been made to solve the above-described technical problems, and an object thereof is to provide an air conditioner using a non-azeotropic refrigerant mixture, which can reduce pressure loss.
Means for solving the problems
An air conditioner is provided with a refrigeration cycle circuit for circulating a non-azeotropic refrigerant mixture, wherein the refrigeration cycle circuit comprises an outdoor unit and an indoor unit, and at least one of the outdoor unit and the indoor unit is provided with a 1 st heat exchanger, a 2 nd heat exchanger, a 1 st gas-liquid two-phase distributor, a 1 st gas distributor, a 2 nd gas-liquid two-phase distributor, a 1 st flow path and a 2 nd flow path. The 1 st heat exchanger includes a 1 st section and a 2 nd section connected in series. The 2 nd heat exchanger includes a 3 rd section and a 4 th section connected in series. The 1 st gas-liquid two-phase distributor is connected to the opposite side of the 1 st part from the side to which the 2 nd part is connected. The 1 st gas distributor is connected to the opposite side of the 2 nd part from the side to which the 1 st part is connected. The 2 nd gas distributor is connected to the opposite side of the 3 rd part from the side to which the 4 th part is connected. The 2 nd gas-liquid two-phase distributor is connected to the side opposite to the side to which the 4 rd part is connected to the 3 rd part. The 1 st flow path includes a portion connecting the 1 st gas distributor, the 2 nd portion, the 1 st portion, and the 1 st gas-liquid two-phase distributor in this order. The 2 nd flow path includes a portion connecting the 2 nd gas distributor, the 3 rd portion, the 4 th portion, and the 2 nd gas-liquid two-phase distributor in this order. The 1 st flow path provided with the 1 st heat exchanger and the 2 nd flow path provided with the 2 nd heat exchanger are connected in parallel to the refrigeration cycle so as to connect the 1 st gas-liquid two-phase distributor and the 2 nd gas-liquid two-phase distributor and to connect the 1 st gas distributor and the 2 nd gas distributor. The evaporator has a 1 st operation mode in which the 1 st heat exchanger and the 2 nd heat exchanger function as condensers, and a 2 nd operation mode in which the 1 st heat exchanger and the 2 nd heat exchanger function as evaporators. In the ventilation direction of the air passing through the 1 st heat exchanger and the 2 nd heat exchanger, respectively, the 1 st part is arranged on the windward side, the 2 nd part is arranged on the leeward side, the 3 rd part is arranged on the windward side, and the 4 th part is arranged on the leeward side.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the air conditioner of the present disclosure, in the 1 st operation mode, the zeotropic mixed refrigerant in the gas state flows into the 1 st gas demultiplexer, becomes the liquid refrigerant in the 1 st heat exchanger, flows through the 1 st gas-liquid two-phase distributor, and in the 2 nd operation mode, the zeotropic mixed refrigerant in the gas state flows into the 2 nd gas demultiplexer, becomes the liquid refrigerant in the 2 nd heat exchanger, and flows through the 2 nd gas-liquid two-phase distributor. In the 2 nd operation mode, the non-azeotropic mixed refrigerant in the gas-liquid two-phase state flows into the 1 st gas-liquid two-phase distributor in the 1 st flow path, the refrigerant in the gas state in the 1 st heat exchanger flows through the 1 st gas demultiplexer, the non-azeotropic mixed refrigerant in the gas-liquid two-phase state flows into the 2 nd gas-liquid two-phase distributor in the 2 nd flow path, and the refrigerant in the gas state in the 2 nd heat exchanger flows through the 1 st gas demultiplexer. This can reduce the pressure loss of the zeotropic refrigerant mixture circulating in the refrigeration cycle.
Drawings
Fig. 1 is a diagram showing a refrigeration cycle of an air conditioner according to embodiment 1.
Fig. 2 is a perspective view schematically showing a structure of an outdoor heat exchanger or the like in the outdoor unit of the embodiment.
Fig. 3 is a perspective view for explaining the flow of the refrigerant in the outdoor heat exchanger and the like at the time of the cooling operation of the embodiment.
Fig. 4 is a perspective view for explaining the flow of refrigerant in the outdoor heat exchanger and the like at the time of heating operation in this embodiment.
Fig. 5 is a diagram including a graph relating to the temperature of the refrigerant and a graph relating to the temperature of the air for explaining the operation and effects of the outdoor heat exchanger and the like at the time of the cooling operation of the embodiment.
Fig. 6 is a diagram including a graph relating to the temperature of the refrigerant and a graph relating to the temperature of the air for explaining the operation and effects of the outdoor heat exchanger and the like at the time of the heating operation of the embodiment.
Fig. 7 is a diagram showing a refrigeration cycle of an air conditioner according to a modification of the present embodiment.
Fig. 8 is a diagram showing a refrigeration cycle of the air conditioner according to embodiment 2.
Fig. 9 is a perspective view schematically showing a structure of an outdoor heat exchanger or the like in the outdoor unit of the embodiment.
Fig. 10 is a perspective view for explaining the flow of the refrigerant in the outdoor heat exchanger and the like at the time of the cooling operation of the embodiment.
Fig. 11 is a perspective view for explaining the flow of refrigerant in the outdoor heat exchanger and the like at the time of the heating operation of the embodiment.
Fig. 12 is a diagram including a graph relating to the temperature of the refrigerant and a graph relating to the temperature of the air for explaining the operation and effects of the outdoor heat exchanger and the like at the time of the cooling operation of the embodiment.
Fig. 13 is a diagram including a graph relating to the temperature of the refrigerant and a graph relating to the temperature of the air for explaining the operation and effects of the outdoor heat exchanger and the like at the time of the heating operation of the embodiment.
Fig. 14 is a diagram showing a refrigeration cycle of the air conditioner according to embodiment 3.
Fig. 15 is a perspective view schematically showing a structure of an outdoor heat exchanger or the like in the outdoor unit of the embodiment.
Fig. 16 is a perspective view for explaining the flow of refrigerant in the outdoor heat exchanger and the like at the time of the cooling operation of the embodiment.
Fig. 17 is a perspective view for explaining the flow of refrigerant in the outdoor heat exchanger and the like at the time of the heating operation of the embodiment.
Fig. 18 is a diagram including a graph relating to the temperature of the refrigerant and a graph relating to the temperature of the air for explaining the operation and effects of the outdoor heat exchanger and the like at the time of the cooling operation of the embodiment.
Fig. 19 is a diagram including a graph relating to the temperature of the refrigerant and a graph relating to the temperature of the air for explaining the operation and effects of the outdoor heat exchanger and the like at the time of the heating operation of the embodiment.
Detailed Description
Embodiment 1.
An example of the air conditioner of embodiment 1 will be described. As shown in fig. 1, the air conditioner 1 includes an outdoor unit 3 and an indoor unit 5. The compressor 7, the four-way valve 9, the outdoor heat exchanger 11, the expansion valve 19, and the like are housed in the outdoor unit 3. The indoor unit 5 accommodates an indoor heat exchanger 27 and the like.
The compressor 7, the four-way valve 9, the outdoor heat exchanger 11, the expansion valve 19, and the indoor heat exchanger 27 are connected by a refrigerant pipe 41 to constitute a refrigeration cycle circuit 51. The refrigerant circulates in the refrigeration cycle 51 (refrigerant pipe 41). In the air conditioner 1, a non-azeotropic refrigerant 43 is used as the refrigerant. The zeotropic mixed refrigerant 43 is a mixed refrigerant in which a plurality of single components are mixed, and is a refrigerant in which a component difference occurs between a gas phase and a liquid phase.
The outdoor heat exchanger 11 and the like will be described in detail. As shown in fig. 1 and 2, the outdoor heat exchanger 11 includes an outdoor 1 st heat exchanger 13 as a 1 st heat exchanger and an outdoor 2 nd heat exchanger 15 as a 2 nd heat exchanger. Here, the outdoor 2 nd heat exchanger 15 is disposed above the outdoor 1 st heat exchanger 13. The outdoor 1 st heat exchanger 13 includes a 1 st portion 13a and a 2 nd portion 13b. The 1 st part 13a and the 2 nd part 13b are connected in series. The 1 st and 2 nd portions 13a and 13b are arranged along the ventilation direction (see arrow YA). The 1 st portion 13a is disposed on the windward side. The 2 nd portion 13b is disposed on the leeward side.
The gas-liquid two-phase distributor 21a serving as the 1 st gas-liquid two-phase distributor is connected to the side opposite to the side to which the 1 st portion 13a and the 2 nd portion 13b are connected. The gas distributor 23a as the 1 st gas distributor is connected to the side opposite to the side to which the 1 st portion 13a is connected with respect to the 2 nd portion 13 b.
The outdoor 2 nd heat exchanger 15 includes a 3 rd portion 15a and a 4 th portion 15b. The 3 rd section 15a and the 4 th section 15b are connected in series. The 3 rd and 4 th portions 15a and 15b are arranged along the ventilation direction (see arrow YA). The 3 rd part 15a is disposed on the windward side. The 4 th portion 15b is disposed on the leeward side.
The gas-liquid two-phase distributor 21b serving as the 2 nd gas-liquid two-phase distributor is connected to the side opposite to the side to which the 4 th portion 15b is connected to the 3 rd portion 15 a. The gas distributor 23b as the 2 nd gas distributor is connected to the opposite side of the 3 rd section 15a from the side to which the 4 th section 15b is connected.
The air conditioner 1 is provided with a flow path R1 as a 1 st flow path, and the flow path R1 includes a portion connecting the gas distributor 23a, the 2 nd portion 13b, the 1 st portion 13a, and the gas-liquid two-phase distributor 21a in this order. A flow path R2 is provided as a 2 nd flow path, and the flow path R2 includes a portion connecting the gas distributor 23b, the 3 rd portion 15a, the 4 th portion 15b, and the gas-liquid two-phase distributor 21b in this order.
The flow path R1 in which the outdoor 1 st heat exchanger 13 is disposed and the flow path R2 in which the outdoor 2 nd heat exchanger 15 is disposed are connected in parallel to the refrigeration cycle 51 so as to connect the gas-liquid two-phase distributor 21a and the gas-liquid two-phase distributor 21b and to connect the gas distributor 23a and the gas distributor 23 b. That is, the flow path R1 and the flow path R2 are connected in parallel to the refrigeration cycle 51 (main flow path) for the zeotropic refrigerant mixture.
Next, the indoor heat exchanger 27 and the like will be described. As shown in fig. 1, the indoor heat exchanger 27 includes an indoor 1 st heat exchanger 29 and an indoor 2 nd heat exchanger 31.
A gas-liquid two-phase distributor 33a is connected to one end side of the indoor 1 st heat exchanger 29. A gas distributor 35a is connected to the other end side of the indoor 1 st heat exchanger 29. A gas-liquid two-phase distributor 33b is connected to one end side of the indoor 2 nd heat exchanger 31. The other end side of the indoor 2 nd heat exchanger 31 is connected to a gas distributor 35b.
The air conditioner 1 is provided with a flow path R3, and the flow path R3 includes a portion connecting the gas distributor 35a, the gas-liquid two-phase distributor 33a, and the indoor 1 st heat exchanger 29 in this order. A flow path R4 is provided, and the flow path R4 includes a portion connecting the gas distributor 35b, the indoor 2 nd heat exchanger 31, and the gas-liquid two-phase distributor 33b in this order.
The flow path R3 in which the indoor 1 st heat exchanger 29 is disposed and the indoor 2 nd heat exchanger 31 in which the indoor 2 nd heat exchanger 31 is disposed are connected in parallel to the refrigeration cycle 51 so as to connect the gas-liquid two-phase distributor 33a and the gas-liquid two-phase distributor 33b and to connect the gas distributor 35a and the gas distributor 35 b. That is, the flow paths R3 and R4 are connected in parallel to the refrigeration cycle 51 (main flow path) through which the zeotropic refrigerant mixture circulates. The air conditioner 1 of embodiment 1 is configured as described above.
Next, the operation (flow of refrigerant) of the air conditioner 1 (refrigeration cycle 51) will be described.
(cooling operation)
First, a cooling operation as the 1 st operation mode will be described as the operation of the air conditioner 1 (the refrigeration cycle 51). In this case, the outdoor heat exchanger 11 in the outdoor unit 3 functions as a condenser, and the indoor heat exchanger 27 in the indoor unit 5 functions as an evaporator.
By driving the compressor 7, the high-temperature and high-pressure gas refrigerant (single-phase) is discharged from the compressor 7. The discharged high-temperature and high-pressure gas refrigerant is sent to the outdoor unit 3 through the four-way valve 9. In the outdoor unit 3, the refrigerant fed flows through the outdoor heat exchanger 11. At this time, the refrigerant flows in parallel in the outdoor 1 st heat exchanger 13 (flow path R1) and the outdoor 2 nd heat exchanger 15 (flow path R2). The flow of the refrigerant in the outdoor heat exchanger 11 will be described in detail later.
In the outdoor heat exchanger 11, heat exchange is performed between the refrigerant flowing in and air supplied by a propeller fan (not shown). The high-temperature and high-pressure gas refrigerant is condensed by heat exchange and becomes a high-pressure liquid refrigerant (single-phase).
The high-pressure liquid refrigerant flowing through the outdoor heat exchanger 11 and sent from the outdoor unit 3 passes through the expansion valve 19 to be a low-pressure gas refrigerant and a liquid refrigerant in a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state is sent to the indoor unit 5. In the indoor unit 5, the refrigerant fed flows through the indoor heat exchanger 27. At this time, the refrigerant flows in parallel in the indoor 1 st heat exchanger 29 (flow path R3) and the indoor 2 nd heat exchanger 31 (flow path R4).
In the indoor heat exchanger 27, heat exchange is performed between the refrigerant in a gas-liquid two-phase state that flows in and the air that is sent to the indoor heat exchanger 27 by a fan (not shown). The refrigerant in the gas-liquid two-phase state evaporates the liquid refrigerant by heat exchange to become a low-pressure gas refrigerant (single-phase). The heat-exchanged air is sent out from the indoor heat exchanger 27 into the room, and the room is cooled.
The low-pressure gas refrigerant flowing through the indoor heat exchanger 27 and sent from the indoor unit 5 flows into the compressor 7 through the four-way valve 9. The low-pressure gas refrigerant flowing into the compressor 7 is compressed to become a high-temperature high-pressure gas refrigerant, and is discharged from the compressor 7 again. The cycle is repeated thereafter.
(heating operation)
As the operation of the air conditioner 1 (refrigeration cycle 51), a heating operation as the 2 nd operation mode will be described. In this case, the indoor heat exchanger 27 in the indoor unit 5 functions as a condenser, and the outdoor heat exchanger 11 in the outdoor unit 3 functions as an evaporator.
By driving the compressor 7, the high-temperature and high-pressure gas refrigerant (single-phase) is discharged from the compressor 7. The discharged high-temperature and high-pressure gas refrigerant (single-phase) is sent to the indoor unit 5 via the four-way valve 9. The refrigerant sent to the indoor unit 5 flows through the indoor heat exchanger 27. At this time, the refrigerant flows in parallel in the indoor 1 st heat exchanger 29 (flow path R3) and the indoor 2 nd heat exchanger 31 (flow path R4).
In the indoor heat exchanger 27, heat exchange is performed between the gas refrigerant flowing in and the air sent by a fan (not shown). The high-temperature and high-pressure gas refrigerant is condensed to become a high-pressure liquid refrigerant (single-phase). The heat-exchanged air is sent out from the indoor heat exchanger 27 into the room, and the room is heated. The high-pressure liquid refrigerant flowing through the indoor heat exchanger 27 and sent from the indoor unit 5 is sent to the outdoor unit.
The high-pressure liquid refrigerant sent to the outdoor unit 3 is converted into a low-pressure gas refrigerant and a liquid refrigerant in a gas-liquid two-phase state by the expansion valve 19. The refrigerant in the gas-liquid two-phase state flows through the outdoor heat exchanger 11. At this time, the refrigerant flows in parallel in the outdoor 1 st heat exchanger 13 (flow path R1) and the outdoor 2 nd heat exchanger 15 (flow path R2).
In the outdoor heat exchanger 11, heat exchange is performed between the refrigerant in a gas-liquid two-phase state flowing in and air supplied by a propeller fan (not shown). The liquid refrigerant in the gas-liquid two-phase refrigerant evaporates to become a low-pressure gas refrigerant (single-phase).
The low-pressure gas refrigerant flowing through the outdoor heat exchanger 11 and sent from the outdoor unit 3 flows into the compressor 7 through the four-way valve 9. The low-pressure gas refrigerant flowing into the compressor 7 is compressed to become a high-temperature high-pressure gas refrigerant, and is discharged from the compressor 7 again. The cycle is repeated thereafter.
(defrosting operation)
In the heating operation, the outdoor heat exchanger 11 functions as an evaporator, and therefore frost may be generated in the outdoor heat exchanger 11. Therefore, in the air conditioner 1, a defrosting operation is performed to remove frost generated in the outdoor heat exchanger 11. In the defrosting operation, by performing the same operation as the cooling operation, the high-temperature and high-pressure refrigerant discharged from the compressor 7 is sent to the outdoor heat exchanger 11, and thereby frost generated in the outdoor heat exchanger 11 is removed.
The general flow of the refrigerant in the air conditioner 1 (refrigeration cycle 51) is as described above. Next, the flow of the refrigerant in the outdoor heat exchanger 11 and the indoor heat exchanger 27 will be described more specifically.
(flow of refrigerant in the outdoor heat exchanger 11 during the cooling operation)
As shown in fig. 1 and 3, the high-temperature and high-pressure gas refrigerant (single-phase) discharged from the compressor 7 is sent to the outdoor unit 3 via the four-way valve 9. In the outdoor unit 3, the refrigerant branches into a flow path R1 and a flow path R2 at a branch junction P1.
In the flow path R1, the high-temperature and high-pressure gas refrigerant flows through the gas distributor 23a, the 2 nd portion 13b, the 1 st portion 13a, and the gas-liquid two-phase distributor 21a in this order. The high-temperature and high-pressure gas refrigerant flows into the gas distributor 23a in the flow path R1, is condensed in the outdoor 1 st heat exchanger 13, becomes a high-pressure liquid refrigerant, and flows through the gas-liquid two-phase distributor 21 a. In the outdoor 1 st heat exchanger 13, the refrigerant flows through the 2 nd portion 13b arranged on the leeward side and then flows as a counter flow through the 1 st portion 13a arranged on the windward side.
In the flow path R2, the high-temperature and high-pressure gas refrigerant flows through the gas distributor 23b, the 3 rd part 15a, the 4 th part 15b, and the gas-liquid two-phase distributor 21b in this order. The high-temperature and high-pressure gas refrigerant flows into the gas distributor 23b in the flow path R2, is condensed in the outdoor 2 nd heat exchanger 15, becomes a high-pressure liquid refrigerant, and flows through the gas-liquid two-phase distributor 21 b. In the outdoor 2 nd heat exchanger 15, the refrigerant flows through the 3 rd portion 15a arranged on the windward side and then flows as a parallel flow through the 4 th portion 15b arranged on the leeward side.
The high-pressure liquid refrigerant flowing through the gas-liquid two-phase distributor 21a and the high-pressure liquid refrigerant flowing through the gas-liquid two-phase distributor 21b merge at the branching and merging point P2, and pass through the expansion valve 19 to become a low-pressure gas refrigerant and a liquid refrigerant in a gas-liquid two-phase state. The low-pressure gas-liquid two-phase refrigerant is sent to the indoor unit 5 (see fig. 1).
(flow of refrigerant in indoor Heat exchanger 27 during Cooling operation)
Next, the flow of the refrigerant in the indoor unit 5 will be briefly described with reference to the outdoor unit 3. As shown in fig. 1, the refrigerant flowing into the indoor unit 5 branches into a flow path R3 and a flow path R4 at a branch junction P4.
In the flow path R3, the refrigerant in the gas-liquid two-phase state flows through the gas-liquid two-phase distributor 33a, the indoor 1 st heat exchanger 29, and the gas distributor 35a in this order. In the flow path R3, the low-pressure gas-liquid two-phase refrigerant flows through the gas-liquid two-phase distributor 33a, evaporates in the indoor 1 st heat exchanger 29, becomes a low-pressure gas refrigerant, and flows through the gas distributor 35 a. In the indoor 1 st heat exchanger 29, the refrigerant flows as parallel flows.
In the flow path R4, the refrigerant in the gas-liquid two-phase state flows through the gas-liquid two-phase distributor 33b, the indoor 2 nd heat exchanger 31, and the gas distributor 35b in this order. In the flow path R4, the low-pressure gas-liquid two-phase refrigerant flows through the gas-liquid two-phase distributor 33b, evaporates in the indoor 2 nd heat exchanger 31, becomes a low-pressure gas refrigerant, and flows through the gas distributor 35b. In the indoor 2 nd heat exchanger 31, the refrigerant flows as a counter flow.
(flow of refrigerant in indoor Heat exchanger 27 during heating operation)
As shown in fig. 1, the high-temperature and high-pressure gas refrigerant (single-phase) discharged from the compressor 7 is sent to the indoor unit 5 via the four-way valve 9. In the indoor unit 5, the refrigerant branches into a flow path R3 and a flow path R4 at a branch junction P3.
In the flow path R3, the gas refrigerant flows through the gas distributor 35a, the indoor 1 st heat exchanger 29, and the gas-liquid two-phase distributor 33a in this order. In the flow path R3, the high-temperature and high-pressure gas refrigerant flows into the gas distributor 35a, condenses in the indoor 1 st heat exchanger 29, becomes a high-pressure liquid refrigerant, and flows through the gas-liquid two-phase distributor 33a. In the indoor 1 st heat exchanger 29, the refrigerant flows as a counter flow.
In the flow path R4, the gas refrigerant flows through the gas distributor 35b, the indoor 2 nd heat exchanger 31, and the gas-liquid two-phase distributor 33b in this order. In the flow path R4, the high-temperature and high-pressure gas refrigerant flows into the gas distributor 35b, condenses in the indoor 2 nd heat exchanger 31, becomes a high-pressure liquid refrigerant, and flows through the gas-liquid two-phase distributor 33b. In the indoor 2 nd heat exchanger 31, the refrigerant flows as parallel flows.
The high-pressure liquid refrigerant flowing through the gas-liquid two-phase distributor 33a and the high-pressure liquid refrigerant flowing through the gas-liquid two-phase distributor 33b are joined at a branching junction point P4, and sent to the outdoor unit 3.
(flow of refrigerant in the outdoor Heat exchanger 11 during heating operation)
Next, the flow of the refrigerant in the outdoor unit 3 will be described. As shown in fig. 4, the high-pressure liquid refrigerant sent to the outdoor unit 3 passes through the expansion valve 19, and is a low-pressure gas refrigerant and a liquid refrigerant in a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state branches into a flow path R1 and a flow path R2 at a branch junction point P2.
In the flow path R1, the refrigerant in the gas-liquid two-phase state flows through the gas-liquid two-phase distributor 21a, the 1 st part 13a, the 2 nd part 13b, and the gas distributor 23a in this order. In the flow path R1, the low-pressure gas-liquid two-phase refrigerant flows through the gas-liquid two-phase distributor 21a, evaporates in the 1 st and 2 nd portions 13a and 13b, becomes a low-pressure gas refrigerant, and flows through the gas distributor 23a. In the outdoor 1 st heat exchanger 13 (1 st portion 13a and 2 nd portion 13 b), the refrigerant flows as parallel flows.
In the flow path R2, the refrigerant in the gas-liquid two-phase state flows through the gas-liquid two-phase distributor 21b, the 3 rd part 15a, the 4 th part 15b, and the gas distributor 23b in this order. In the flow path R2, the low-pressure gas-liquid two-phase refrigerant flows through the gas-liquid two-phase distributor 21b, evaporates in the 4 th and 3 rd sections 15b and 15a, becomes a low-pressure gas refrigerant, and flows through the gas distributor 23b. In the outdoor 2 nd heat exchanger 15 (4 th and 3 rd sections 15b and 15 a), the refrigerant flows as a counter flow.
In the air conditioner 1 in which the zeotropic refrigerant mixture is circulated, the refrigerant in the gas-liquid two-phase state flows through the gas-liquid two-phase distributors 21a, 21b, 33a, and 33b and then flows through the corresponding outdoor heat exchanger 11 or indoor heat exchanger 27, respectively, during the cooling operation and the heating operation, and is converted into the gas refrigerant. The refrigerant that becomes the gas refrigerant in the corresponding outdoor heat exchanger 11 or indoor heat exchanger 27 flows through the gas distributors 23a, 23b, 35a, 35b. This can reduce pressure loss and the like. This will be described.
First, in general, when the heat exchanger functions as an evaporator, a gas-liquid two-phase distributor is disposed on the inlet side of the refrigerant of the heat exchanger so as to uniformly distribute the refrigerant in the gas-liquid two-phase state of the gas refrigerant and the liquid refrigerant flowing into the heat exchanger. An orifice is disposed in the gas-liquid two-phase distributor, for example, so as to uniformly distribute the refrigerant in the gas-liquid two-phase state.
On the other hand, when the heat exchanger functions as a condenser, a gas distributor (gas header) having a relatively large volume is disposed on the refrigerant inlet side of the heat exchanger in order to suppress pressure loss of the gas refrigerant flowing into the heat exchanger.
In a heat exchanger of an air conditioner using a general refrigerant other than a non-azeotropic mixed refrigerant, when the heat exchanger functions as a condenser and when the heat exchanger functions as an evaporator, the flow direction of the refrigerant flowing through the heat exchanger is reversed. Therefore, a gas-liquid two-phase distributor is disposed on one side of the heat exchanger, and a gas distributor is disposed on the other side.
In contrast, in the heat exchangers of the comparative examples (patent document 1 and patent document 2) using the zeotropic refrigerant mixture, the flow direction of the refrigerant is the same in the case where the heat exchanger functions as a condenser and in the case where the heat exchanger functions as an evaporator.
Here, it is assumed that a gas-liquid two-phase distributor is disposed on one side of the heat exchanger and a gas distributor is disposed on the other side of the heat exchanger.
When the heat exchanger functions as an evaporator, the refrigerant in the gas-liquid two-phase state flows through the gas-liquid two-phase distributor, and then exchanges heat in the heat exchanger to become a gas refrigerant, and flows through the gas distributor. On the other hand, when the heat exchanger functions as a condenser, the gas refrigerant flows through the gas-liquid two-phase distributor, and then exchanges heat in the heat exchanger to become a liquid refrigerant, and flows through the gas distributor (case 1).
Therefore, particularly when the heat exchanger functions as a condenser, the gas refrigerant flows through the gas-liquid two-phase distributor that distributes the refrigerant in the gas-liquid two-phase state equally, and therefore, the pressure loss of the refrigerant increases. In addition, the liquid refrigerant flows through the gas header having a relatively large volume, and thus, an increase in the amount of refrigerant is caused.
Next, it is assumed that a gas header is disposed on one side of the heat exchanger and a gas-liquid two-phase distributor is disposed on the other side of the heat exchanger.
When the heat exchanger functions as a condenser, the gas refrigerant flows through the gas distributor, and then exchanges heat in the heat exchanger to become a liquid refrigerant, and flows through the gas-liquid two-phase distributor. On the other hand, when the heat exchanger functions as an evaporator, the refrigerant in a gas-liquid two-phase state flows through the gas distributor, and then, is subjected to heat exchange in the heat exchanger to become a gas refrigerant, and flows through the gas-liquid two-phase distributor (case 2).
Therefore, particularly when the heat exchanger functions as an evaporator, the refrigerant in a gas-liquid two-phase state flows through the gas header having a relatively large volume, and therefore, the refrigerant cannot be equally distributed, and the performance as an evaporator is lowered. Further, the gas refrigerant flows through the gas-liquid two-phase distributor that equally distributes the refrigerant in the gas-liquid two-phase state, and therefore, the pressure loss of the refrigerant increases.
In the air conditioner of the comparative example, the direction in which the refrigerant flows through the refrigerant pipe connecting the indoor unit and the outdoor unit is the same in the cooling operation and the heating operation. In the cooling operation, in order to send the gas refrigerant flowing through the indoor unit to the outdoor unit, a refrigerant pipe having a relatively large pipe diameter has to be used as the refrigerant pipe to suppress the pressure loss. On the other hand, during the heating operation, the liquid refrigerant flowing through the indoor unit flows through the refrigerant pipe having a relatively large pipe diameter. Therefore, the liquid refrigerant is likely to remain in the refrigerant pipe, and the amount of refrigerant increases.
The heat exchanger in the air conditioner 1 described above can obtain the following effects with respect to the air conditioner of the comparative example.
First, a case of the cooling operation as the 1 st operation mode will be described. In this case, in the outdoor unit 3 (outdoor heat exchanger 11), the gas refrigerant flows through the gas distributors 23a and 23b for distributing the gas appropriately, and then exchanges heat in the corresponding outdoor 1 st heat exchanger 13 or outdoor 2 nd heat exchanger 15 to become a liquid refrigerant, and flows through the gas-liquid two-phase distributors 21a and 21b.
Next, in the indoor unit 5 (indoor heat exchanger 27), the refrigerant in the gas-liquid two-phase state flows through gas-liquid two-phase distributors 33a and 33b each provided with a distributor (distributor) for uniformly distributing the refrigerant in the gas-liquid two-phase state, and then exchanges heat in the corresponding indoor 1 st heat exchanger 29 or indoor 2 nd heat exchanger 31 to become a gas refrigerant, and flows through the gas distributors 35a and 35b.
Thus, the gas refrigerant does not flow through the gas-liquid two-phase distributor as in case 1 of the comparative example, and the pressure loss of the refrigerant can be reduced. In addition, the liquid refrigerant does not flow through the gas distributor having a relatively large volume, and an increase in the amount of refrigerant can be prevented.
Next, a heating operation as the 2 nd operation mode will be described. In this case, first, in the indoor unit 5 (indoor heat exchanger 27), the gas refrigerant flows through the gas distributors 35a and 35b for distributing the gas appropriately, and then, is subjected to heat exchange in the corresponding indoor 1 st heat exchanger 29 or indoor 2 nd heat exchanger 31 to become a liquid refrigerant, and flows through the gas-liquid two-phase distributors 33a and 33b.
Next, in the outdoor unit 3 (outdoor heat exchanger 11), the refrigerant in the gas-liquid two-phase state flows through the gas-liquid two-phase distributors 21a and 21b which uniformly distribute the refrigerant in the gas-liquid two-phase state, and then exchanges heat in the corresponding outdoor 1 st heat exchanger 13 or outdoor 2 nd heat exchanger 15 to become a gas refrigerant, and flows through the gas distributors 23a and 23b.
Thus, as in case 2 of the comparative example, the refrigerant in the gas-liquid two-phase state does not flow through the gas distributor having a relatively large volume and is not equally distributed, and the performance as an evaporator can be ensured. In addition, the gas refrigerant does not flow through the gas-liquid two-phase distributor, and the pressure loss of the refrigerant can be reduced. Further, the gas refrigerant does not flow through the gas-liquid two-phase distributor but flows through the gas distributor, whereby an excessive rise in high pressure can be suppressed.
In the air conditioner 1 described above, the direction in which the refrigerant flows through the refrigerant pipe 41 connecting the indoor unit 5 and the outdoor unit 3 is reversed during the cooling operation and the heating operation. As a result, as in the air conditioner of the comparative example, it is not necessary to increase the pipe diameter of the refrigerant pipe 41 connecting the indoor unit 5 and the outdoor unit 3 in consideration of the cooling operation, and the liquid refrigerant can be suppressed from accumulating in the refrigerant pipe 41 even in the heating operation, and the increase in the refrigerant amount can be suppressed.
Next, the effect of the counter flow in the air conditioner 1 will be described. Here, the outdoor heat exchanger 11 will be described as an example.
First, the cooling operation in the 1 st operation mode will be described. Fig. 5 shows graphs GR1 and GR2 related to the temperature of the refrigerant flowing through the outdoor heat exchanger 11 and graphs GA1 and GA2 related to the temperature of the air passing through the outdoor heat exchanger 11 during the cooling operation. The outdoor heat exchanger 11 and the like shown in fig. 3 are collectively shown at the upper layer.
As shown in fig. 5, a graph GR1 shows a relationship between the flow (direction) of air and the temperature of the refrigerant flowing in the outdoor 1 st heat exchanger 13. The temperature of the refrigerant immediately before flowing into the outdoor 1 st heat exchanger 13 is a temperature TAin, and the temperature of the refrigerant immediately after flowing through the outdoor 1 st heat exchanger 13 is a temperature TAout.
The graph GR2 shows the relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 2 nd heat exchanger 15. The temperature of the refrigerant immediately before flowing into the outdoor 2 nd heat exchanger 15 is a temperature TBin, and the temperature of the refrigerant immediately after flowing through the outdoor 2 nd heat exchanger 15 is a temperature TBout.
The graph GA1 shows the relationship between the flow (direction) of air and the temperature of air passing through the outdoor 1 st heat exchanger 13. The graph GA2 shows the relationship between the flow (direction) of air and the temperature of the air passing through the outdoor 2 nd heat exchanger 15.
As shown in the upper layer of fig. 5, in the outdoor 1 st heat exchanger 13 of the outdoor heat exchanger 11, the refrigerant flows in a counter flow so as to oppose the flow of air (arrow YA). In the outdoor 2 nd heat exchanger 15, the refrigerant becomes a parallel flow that flows in parallel with the flow of air (arrow YA).
The non-azeotropic refrigerant mixture has the following properties: in the two-phase state, the dryness decreases and the temperature decreases. As shown in the graph GR1, the temperature of the refrigerant flowing in the opposite direction to the flow direction of the air decreases. On the other hand, as shown in graph GR2, the refrigerant that becomes parallel flow decreases in temperature as it flows in the same direction as the flow direction of air.
On the other hand, as shown in the graphs GA1 and GA2, the air passing through the outdoor heat exchanger 11 increases in temperature by heat exchange with the refrigerant. Therefore, in the refrigerant that becomes parallel flow, the temperature difference between the temperature of the refrigerant and the temperature of the air gradually becomes smaller. In the case of the refrigerant that is a counter-flow, a temperature difference between the temperature of the refrigerant and the temperature of the air can be ensured as compared with the case of the refrigerant that is a parallel flow.
Thus, in the outdoor heat exchanger 11, the temperature of the air passing through the outdoor 1 st heat exchanger 13 is higher than the temperature of the air passing through the outdoor 2 nd heat exchanger 15, and in the outdoor heat exchanger 11, particularly in the outdoor 1 st heat exchanger 13, the heat exchange amount of the refrigerant and the air increases. As a result, the performance of the air conditioner 1 during cooling operation can be improved.
Next, a heating operation in the 2 nd operation mode will be described. Fig. 6 shows graphs GR1 and GR2 related to the temperature of the refrigerant flowing through the outdoor heat exchanger 11 and graphs GA1 and GA2 related to the temperature of the air passing through the outdoor heat exchanger 11 during the heating operation. The outdoor heat exchanger 11 and the like shown in fig. 4 are collectively shown at the upper layer.
As shown in fig. 6, a graph GR1 shows a relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 1 st heat exchanger 13. The temperature of the refrigerant immediately before flowing into the outdoor 1 st heat exchanger 13 is a temperature TAin, and the temperature of the refrigerant immediately after flowing through the outdoor 1 st heat exchanger 13 is a temperature TAout.
The graph GR2 shows the relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 2 nd heat exchanger 15. The temperature of the refrigerant immediately before flowing into the outdoor 2 nd heat exchanger 15 is a temperature TBin, and the temperature of the refrigerant immediately after flowing through the outdoor 2 nd heat exchanger 15 is a temperature TBout.
The graph GA1 shows the relationship between the flow (direction) of air and the temperature of air passing through the outdoor 1 st heat exchanger 13. The graph GA2 shows the relationship between the flow (direction) of air and the temperature of the air passing through the outdoor 2 nd heat exchanger 15.
As shown in the upper layer of fig. 6, in the outdoor 1 st heat exchanger 13 of the outdoor heat exchanger 11, the refrigerant becomes a parallel flow that flows in parallel with the flow of air (arrow YA). In the outdoor 2 nd heat exchanger 15, the refrigerant is a counter flow that flows in opposition to the flow of air (arrow YA).
As described above, in the refrigerant that becomes parallel flow, the temperature difference between the temperature of the refrigerant and the temperature of the air gradually becomes smaller. In the case of the refrigerant that is a counter-flow, a temperature difference between the temperature of the refrigerant and the temperature of the air can be ensured as compared with the case of the refrigerant that is a parallel flow.
Thereby, in the outdoor heat exchanger 11, the temperature of the air passing through the outdoor 2 nd heat exchanger 15 is lower than the temperature of the air passing through the outdoor 1 st heat exchanger 13, and in the outdoor heat exchanger 11, particularly in the outdoor 2 nd heat exchanger 15, the heat exchange amount of the refrigerant and the air increases. As a result, the performance of the air conditioner 1 during heating operation can be improved.
In the air conditioner 1 described above, the outdoor 1 st heat exchanger 13 and the outdoor 2 nd heat exchanger 15 are connected in parallel to the refrigeration cycle 51. The indoor 1 st heat exchanger 13 and the outdoor 2 nd heat exchanger 15 are connected in parallel to the refrigeration cycle 51.
Then, as shown in fig. 7, a Y-shaped or T-shaped branching portion 61 may be provided at each of the branching and merging points P1 and P2 so that the refrigerant is equally distributed (merged) to the outdoor 1 st heat exchanger 13 and the outdoor 2 nd heat exchanger 15. Similarly, the Y-shaped or T-shaped branching portions 61 may be provided at the branching and merging points P3 and P4, respectively, so that the refrigerant is equally distributed (merged) to the indoor 1 st heat exchanger 29 and the indoor 2 nd heat exchanger 31.
Embodiment 2.
An example of the air conditioner of embodiment 2 will be described. As shown in fig. 8 and 9, the outdoor heat exchanger 11 includes an outdoor 3 rd heat exchanger 17 as a 3 rd heat exchanger in addition to the outdoor 1 st heat exchanger 13 and the outdoor 2 nd heat exchanger 15. The outdoor 3 rd heat exchanger 17 is connected in series with the refrigeration cycle 51 between the expansion valve 19 and the outdoor 1 st heat exchanger 13 and the outdoor 2 nd heat exchanger 15 connected in parallel. The outdoor 1 st heat exchanger 13 is disposed below the outdoor 1 st heat exchanger 13 and the outdoor 2 nd heat exchanger 15.
The number of refrigerant channels in the outdoor 1 st heat exchanger 13 is the 1 st number of refrigerant channels, the number of refrigerant channels in the outdoor 2 nd heat exchanger 15 is the 2 nd number of refrigerant channels, and the number of refrigerant channels in the outdoor 3 rd heat exchanger 17 is the 3 rd number of refrigerant channels. The 3 rd refrigerant flow path number is smaller than the 1 st refrigerant flow path number and the 2 nd refrigerant flow path number.
The outdoor 3 rd heat exchanger 17 includes a 5 th portion 17a and a 6 th portion 17b. The 5 th portion 17a and the 6 th portion 17b are connected in series. The 5 th and 6 th portions 17a and 17b are arranged along the ventilation direction (see arrow YA). The 5 th portion 17a is disposed on the windward side. The 6 th portion 17b is disposed on the leeward side.
The gas-liquid two-phase distributor 21c serving as the 3 rd gas-liquid two-phase distributor is connected to the side opposite to the side to which the 5 th portion 17a and the 6 th portion 17b are connected. The gas distributor 23c as the 3 rd gas distributor is connected to the side opposite to the side to which the 5 th portion 17a is connected with respect to the 6 th portion 17 b.
The air conditioner 1 is provided with a flow path R5 as a 3 rd flow path, and the flow path R5 includes a portion connecting the gas distributor 23c, the 6 th portion 17b, the 5 th portion 17a, and the gas-liquid two-phase distributor 21c in this order. Since the other structures are the same as those of the air conditioner 1 shown in fig. 1 and 2, the same reference numerals are given to the same components, and the description thereof will not be repeated unless necessary.
Next, the operation (flow of refrigerant) of the air conditioner 1 (refrigeration cycle 51) will be described. The description is simplified for the operation repeated with the operation of the air conditioner 1 according to embodiment 1.
(cooling operation)
First, the cooling operation will be described. As shown in fig. 8 and 10, the high-temperature and high-pressure gas refrigerant discharged from the compressor 7 is sent to the outdoor unit 3 through the four-way valve 9. The refrigerant sent to the outdoor unit 3 flows through the outdoor 1 st heat exchanger 13 (flow path R1) and the outdoor 2 nd heat exchanger 15 (flow path R2) in parallel, and then flows through the indoor 3 rd heat exchanger 17 (flow path R5).
In the outdoor unit 3, the refrigerant flows through the flow path R1 and the flow path R2 in parallel, and then merges at the branching and merging point P2, and flows through the flow path R5. In the flow path R5, the refrigerant flows through the gas distributor 23c, the 6 th portion 17b, the 5 th portion 17a, and the gas-liquid two-phase distributor 21c in this order. In the outdoor 3 rd heat exchanger 17, the refrigerant flows through the 6 th portion 17b arranged on the leeward side and then flows as a counter flow through the 5 th portion 17a arranged on the windward side.
The refrigerant (high-pressure liquid refrigerant) flowing through the outdoor unit 3 is a low-pressure gas refrigerant and a low-pressure liquid refrigerant in a gas-liquid two-phase state via the expansion valve 19. The low-pressure gas-liquid two-phase refrigerant flows into the indoor unit 5, becomes a low-pressure gas refrigerant, and enters the compressor 7. The cycle is repeated thereafter.
(heating operation)
Next, the heating operation will be described. As shown in fig. 8 and 11, the high-temperature and high-pressure gas refrigerant discharged from the compressor 7 flows into the indoor unit 5 through the four-way valve 9, and becomes a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is sent to the outdoor unit 3, and is converted into a low-pressure gas refrigerant and a liquid refrigerant in a gas-liquid two-phase state through the expansion valve 19.
After flowing through the outdoor 3 rd heat exchanger (flow path R5), the refrigerant in the gas-liquid two-phase state flows in parallel between the outdoor 1 st heat exchanger 13 (flow path R1) and the outdoor 2 nd heat exchanger 15 (flow path R2). In the flow path R5, the refrigerant flows through the gas-liquid two-phase distributor 21c, the 5 th portion 17a, the 6 th portion 17b, and the gas distributor 23c in this order. In the outdoor 3 rd heat exchanger 17, the refrigerant flows through the 5 th portion 17a arranged on the windward side and then flows as a parallel flow through the 6 th portion 17b arranged on the leeward side.
The low-pressure gas refrigerant flowing through the outdoor 3 heat exchanger 17 and the like and sent from the outdoor unit 3 flows into the compressor 7 through the four-way valve 9. The cycle is repeated thereafter.
In the air conditioner 1 described above, the effect of suppressing the pressure loss of the refrigerant and the effect of suppressing the increase in the amount of the refrigerant can be obtained as in the description of the air conditioner 1 of embodiment 1. In the air conditioner 1 of embodiment 2, the following effects can be obtained.
First, a case of the cooling operation will be described. Fig. 12 shows graphs GR1, GR2, and GR3 related to the temperature of the refrigerant flowing through the outdoor heat exchanger 11 and graphs GA1, GA2, and GA3 related to the temperature of the air passing through the outdoor heat exchanger 11 in the cooling operation. The outdoor heat exchanger 11 and the like shown in fig. 10 are collectively shown at the upper layer.
As shown in fig. 12, a graph GR1 shows a relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 1 st heat exchanger 13. The temperature of the refrigerant immediately before flowing into the outdoor 1 st heat exchanger 13 is a temperature TAin, and the temperature of the refrigerant immediately after flowing through the outdoor 1 st heat exchanger 13 is a temperature TAout.
The graph GR2 shows the relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 2 nd heat exchanger 15. The temperature of the refrigerant immediately before flowing into the outdoor 2 nd heat exchanger 15 is a temperature TBin, and the temperature of the refrigerant immediately after flowing through the outdoor 2 nd heat exchanger 15 is a temperature TBout.
The graph GR3 shows the relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 3 rd heat exchanger 17. The temperature of the refrigerant immediately before flowing into the outdoor 3 rd heat exchanger 17 is the temperature TCin, and the temperature of the refrigerant immediately after flowing through the outdoor 3 rd heat exchanger 17 is the temperature TCout.
The graph GA1 shows the relationship between the flow (direction) of air and the temperature of air passing through the outdoor 1 st heat exchanger 13. The graph GA2 shows the relationship between the flow (direction) of air and the temperature of the air passing through the outdoor 2 nd heat exchanger 15. The graph GA3 shows the relationship between the flow (direction) of air and the temperature of the air passing through the outdoor 3 rd heat exchanger 17.
As shown in the upper layer of fig. 12, in the outdoor 1 st heat exchanger 13 of the outdoor heat exchanger 11, the refrigerant flows in a counter flow so as to oppose the flow of air (arrow YA). In the outdoor 2 nd heat exchanger 15, the refrigerant becomes a parallel flow that flows in parallel with the flow of air (arrow YA). In the outdoor 3 rd heat exchanger 17, the refrigerant is a counter flow that flows in opposition to the flow of air (arrow YA).
On the other hand, as shown in graphs GA1 to GA3, the temperature of the air passing through the outdoor heat exchanger 11 increases by heat exchange with the refrigerant. Therefore, in the refrigerant that becomes parallel flow, the temperature difference between the temperature of the refrigerant and the temperature of the air gradually becomes smaller. In the case of the refrigerant that is a counter-flow, a temperature difference between the temperature of the refrigerant and the temperature of the air can be ensured as compared with the case of the refrigerant that is a parallel flow.
The refrigerant flowing through the outdoor 1 st heat exchanger 13 flows into the outdoor 3 rd heat exchanger 17 as a parallel flow through the outdoor 2 nd heat exchanger 15. In the outdoor 3 rd heat exchanger 17, the refrigerant flows as a counter flow.
That is, the refrigerant including the refrigerant flowing through the outdoor 2 nd heat exchanger 15 so that the temperature difference between the temperature of the refrigerant and the temperature of the air gradually becomes smaller flows as a counter flow in the outdoor 3 rd heat exchanger 17. This ensures a temperature difference between the temperature of the refrigerant and the temperature of the air, and increases the amount of heat exchange between the refrigerant and the air in the outdoor 3 rd heat exchanger 17. As a result, the performance during the cooling operation can be further improved.
Next, the heating operation will be described. Fig. 13 shows graphs GR1, GR2, and GR3 related to the temperature of the refrigerant flowing through the outdoor heat exchanger 11 and graphs GA1, GA2, and GA3 related to the temperature of the air passing through the outdoor heat exchanger 11 during the heating operation. The outdoor heat exchanger 11 and the like shown in fig. 11 are collectively shown at the upper layer.
As shown in fig. 13, a graph GR1 shows a relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 1 st heat exchanger 13. The temperature of the refrigerant immediately before flowing into the outdoor 1 st heat exchanger 13 is a temperature TAin, and the temperature of the refrigerant immediately after flowing through the outdoor 1 st heat exchanger 13 is a temperature TAout.
The graph GR2 shows the relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 2 nd heat exchanger 15. The temperature of the refrigerant immediately before flowing into the outdoor 2 nd heat exchanger 15 is a temperature TBin, and the temperature of the refrigerant immediately after flowing through the outdoor 2 nd heat exchanger 15 is a temperature TBout.
The graph GR3 shows the relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 3 rd heat exchanger 17. The temperature of the refrigerant immediately before flowing into the outdoor 3 rd heat exchanger 17 is the temperature TCin, and the temperature of the refrigerant immediately after flowing through the outdoor 3 rd heat exchanger 17 is the temperature TCout.
The graph GA1 shows the relationship between the flow (direction) of air and the temperature of air passing through the outdoor 1 st heat exchanger 13. The graph GA2 shows the relationship between the flow (direction) of air and the temperature of the air passing through the outdoor 2 nd heat exchanger 15. The graph GA3 shows the relationship between the flow (direction) of air and the temperature of the air passing through the outdoor 3 rd heat exchanger 17.
As shown in the upper layer of fig. 13, in the outdoor 1 st heat exchanger 13 of the outdoor heat exchangers 11, the refrigerant flows as parallel flows. In the outdoor 2 nd heat exchanger 15, the refrigerant flows as a counter flow. In the outdoor 3 rd heat exchanger 17, the refrigerant flows as parallel flows.
On the other hand, as shown in the graphs GA1 to GA3, the temperature of the air passing through the outdoor heat exchanger 11 decreases by heat exchange with the refrigerant.
The refrigerant sent to the outdoor unit 3 and passed through the expansion valve 19 to be in a gas-liquid two-phase state flows through the outdoor 3 rd heat exchanger 17, and then flows in parallel through the outdoor 1 st heat exchanger 13 and the outdoor 2 nd heat exchanger 15. In the outdoor 3 rd heat exchanger 17, the refrigerant in a gas-liquid two-phase state flows as parallel flows.
The 3 rd refrigerant flow path number of the outdoor 3 rd heat exchanger 17 is smaller than the 1 st refrigerant flow path number of the outdoor 1 st heat exchanger 13 and the 2 nd refrigerant flow path number of the outdoor 2 nd heat exchanger 15. Therefore, in the outdoor 3 rd heat exchanger 17, the pressure loss of the refrigerant is relatively high with respect to the outdoor 1 st heat exchanger 13 and the outdoor 2 nd heat exchanger 15.
Thus, the temperature of the refrigerant flowing through the outdoor 3 rd heat exchanger 17 (see the graph GR 3) is higher than the temperature of the refrigerant flowing through the outdoor 1 st heat exchanger 13 (see the graph GR 1) and the temperature of the refrigerant flowing through the outdoor 2 nd heat exchanger 15 (see the graph GR 2).
The outdoor 3 rd heat exchanger 17 is disposed below the outdoor 1 st heat exchanger 13 and the outdoor 2 nd heat exchanger 15. During the heating operation, dew condensation water adhering to the outdoor 1 st heat exchanger 13 and the outdoor 2 nd heat exchanger 15 falls to the outdoor 3 rd heat exchanger 17 arranged below, and frost is easily generated in the outdoor 3 rd heat exchanger 17.
By flowing the refrigerant having a higher temperature than the temperature of the refrigerant flowing through the outdoor 1 st heat exchanger 13 and the temperature of the refrigerant flowing through the outdoor 2 nd heat exchanger 15 to the outdoor 3 rd heat exchanger 17, it is possible to suppress the formation of frost in the outdoor 3 rd heat exchanger 17.
Embodiment 3.
An example of the air conditioner of embodiment 3 will be described. As shown in fig. 14 and 15, the outdoor unit 3 is provided with an outdoor 1 st flow rate adjustment valve 25a and an outdoor 2 nd flow rate adjustment valve 25b.
The outdoor 1 st flow rate adjustment valve 25a is disposed in the flow path R1. The outdoor 1 st flow rate adjustment valve 25a is disposed at a portion between the branching and converging point P2 of the flow path R1 and the gas-liquid two-phase distributor 21 a. The outdoor 2 nd flow rate adjustment valve 25b is disposed in the flow path R2. The outdoor 2 nd flow rate adjustment valve 25b is disposed at a portion between the branching and converging point P2 of the flow path R2 and the gas-liquid two-phase distributor 21 b.
The indoor unit 5 is provided with an indoor 1 st flow rate adjustment valve 37a and an indoor 2 nd flow rate adjustment valve 37b. The 1 st flow rate control valve 37a is disposed in the flow path R3. The indoor 1 st flow rate adjustment valve 37a is disposed at a portion between the branching and converging point P4 of the flow path R3 and the gas-liquid two-phase distributor 33 a. The indoor 2 nd flow rate adjustment valve 37b is disposed in the flow portion between the branch junction P4 of the path R4 and the gas-liquid two-phase distributor 33 b.
As the outdoor 1 st flow rate adjustment valve 25a, the outdoor 2 nd flow rate adjustment valve 25b, the indoor 1 st flow rate adjustment valve 37a, and the indoor 2 nd flow rate adjustment valve 37b, for example, solenoid valves or electronic expansion valves can be used. In the case of using an electronic expansion valve, the expansion valve 19 may be omitted. The configuration other than this is the same as that of the air conditioner 1 shown in fig. 1 and 2, and therefore the same reference numerals are given to the same components, and the description thereof will not be repeated unless necessary.
Next, the operation (flow of refrigerant) of the air conditioner 1 (refrigeration cycle 51) will be described. The description will be simplified with respect to the operation repeated with the operation of the air conditioner 1 of embodiment 1.
(cooling operation)
First, the cooling operation will be described. As shown in fig. 14 and 16, the high-temperature and high-pressure gas refrigerant discharged from the compressor 7 is sent to the outdoor unit 3 through the four-way valve 9. The refrigerant sent to the outdoor unit 3 flows in parallel through the flow path R1 (the outdoor 1 st heat exchanger 13) and the flow path R2 (the outdoor 2 nd heat exchanger 15).
In the flow path R1, the refrigerant flows through the gas distributor 23a, the 2 nd portion 13b, the 1 st portion 13a, the gas-liquid two-phase distributor 21a, and the outdoor 1 st flow rate adjustment valve 25a in this order. In the outdoor 1 st heat exchanger 13, the refrigerant flows through the 2 nd portion 13b arranged on the leeward side and then flows as a counter flow through the 1 st portion 13a arranged on the windward side.
In the flow path R2, the refrigerant flows through the gas distributor 23b, the 3 rd portion 15a, the 4 th portion 15b, the gas-liquid two-phase distributor 21b, and the outdoor 2 nd flow rate adjustment valve 25b in this order. In the outdoor 2 nd heat exchanger 15, the refrigerant flows through the 3 rd portion 15a arranged on the windward side and then flows as a parallel flow through the 4 th portion 15b arranged on the leeward side.
The refrigerant flowing through the flow path R1 merges with the refrigerant flowing through the flow path R2, and passes through the expansion valve 19 to become a low-pressure gas refrigerant and a liquid refrigerant in a gas-liquid two-phase state. The low-pressure gas-liquid two-phase refrigerant is sent to the indoor unit 5. The refrigerant sent to the indoor unit 5 flows in parallel through the flow path R3 (the indoor 1 st heat exchanger 29) and the flow path R4 (the indoor 2 nd heat exchanger 31).
In the flow path R3, the refrigerant flows through the indoor 1 st flow rate adjustment valve 37a, the gas-liquid two-phase distributor 33a, the indoor 1 st heat exchanger 29, and the gas distributor 35a in this order. In the indoor 1 st heat exchanger 29, the refrigerant flows as parallel flows. In the flow path R4, the refrigerant flows through the indoor 2 nd flow rate adjustment valve 37b, the gas-liquid two-phase distributor 33b, the indoor 2 nd heat exchanger 31, and the gas distributor 35b in this order. In the indoor 2 nd heat exchanger 31, the refrigerant flows as a counter flow.
The refrigerant flowing through the flow path R3 merges with the refrigerant flowing through the flow path R4, and flows into the compressor 7. The cycle is repeated thereafter.
(heating operation)
Next, the heating operation will be described. As shown in fig. 14 and 17, the high-temperature and high-pressure gas refrigerant discharged from the compressor 7 is sent to the indoor unit 5 via the four-way valve 9. In the indoor unit 5, the refrigerant flows in parallel in the flow path R3 (the indoor 1 st heat exchanger 29) and the flow path R4 (the indoor 2 nd heat exchanger 31).
In the flow path R3, the refrigerant flows through the gas distributor 35a, the indoor 1 st heat exchanger 29, the gas-liquid two-phase distributor 33a, and the indoor 1 st flow rate adjustment valve 37a in this order. In the indoor 1 st heat exchanger 29, the refrigerant flows as a counter flow. In the flow path R4, the refrigerant flows through the gas distributor 35b, the indoor 2 nd heat exchanger 31, the gas-liquid two-phase distributor 33b, and the indoor 2 nd flow rate adjustment valve 37b in this order. In the indoor 2 nd heat exchanger 31, the refrigerant flows as parallel flows.
The refrigerant flowing through the flow path R3 merges with the refrigerant flowing through the flow path R4, and is sent to the outdoor unit 3, and passes through the expansion valve 19 to become a low-pressure gas refrigerant and a liquid refrigerant in a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state flows in parallel through the flow path R1 (the outdoor 1 st heat exchanger 13) and the flow path R2 (the outdoor 2 nd heat exchanger 15).
In the flow path R1, the refrigerant flows through the outdoor 1 st flow rate adjustment valve 25a, the gas-liquid two-phase distributor 21a, the 1 st portion 13a, the 2 nd portion 13b, and the gas distributor 23a in this order. In the outdoor 1 st heat exchanger 13, the refrigerant flows as parallel flows. In the flow path R2, the refrigerant flows through the outdoor 2 nd flow rate adjustment valve 25b, the gas-liquid two-phase distributor 21b, the 4 th portion 15b, the 3 rd portion 15a, and the gas distributor 23b in this order. In the outdoor 2 nd heat exchanger 15, the refrigerant flows as a counter flow.
The refrigerant flowing through the flow path R1 and the flow path R2 merge, and flow into the compressor 7 through the four-way valve 9. The cycle is repeated thereafter.
In the air conditioner 1 described above, the effect of suppressing the pressure loss of the refrigerant and the effect of suppressing the increase in the amount of the refrigerant can be obtained as in the description of the air conditioner 1 of embodiment 1. In the air conditioner 1 of embodiment 3, the following effects are also obtained.
First, a case of the cooling operation will be described. Fig. 18 shows graphs GR1 and GR2 related to the temperature of the refrigerant flowing through the outdoor heat exchanger 11 and graphs GA1 and GA2 related to the temperature of the air passing through the outdoor heat exchanger 11 during the cooling operation. The outdoor heat exchanger 11 and the like shown in fig. 16 are collectively shown at the upper layer.
As shown in fig. 18, a graph GR1 shows a relationship between the flow (direction) of air and the temperature of the refrigerant flowing in the outdoor 1 st heat exchanger 13. The temperature of the refrigerant immediately before flowing into the outdoor 1 st heat exchanger 13 is a temperature TAin, and the temperature of the refrigerant immediately after flowing through the outdoor 1 st heat exchanger 13 is a temperature TAout.
The graph GR2 shows the relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 2 nd heat exchanger 15. The temperature of the refrigerant immediately before flowing into the outdoor 2 nd heat exchanger 15 is a temperature TBin, and the temperature of the refrigerant immediately after flowing through the outdoor 2 nd heat exchanger 15 is a temperature TBout.
The graph GA1 shows the relationship between the flow (direction) of air and the temperature of air passing through the outdoor 1 st heat exchanger 13. The graph GA2 shows the relationship between the flow (direction) of air and the temperature of the air passing through the outdoor 2 nd heat exchanger 15.
As shown in the upper layer of fig. 18, in the outdoor 1 st heat exchanger 13, the refrigerant flows as a counter flow. In the outdoor 2 nd heat exchanger 15, the refrigerant flows as parallel flows.
On the other hand, as shown in graphs GA1 and GA2, the temperature of the air passing through the outdoor heat exchanger 11 increases by heat exchange with the refrigerant. Therefore, in the refrigerant flowing as the parallel flow, the temperature difference between the temperature of the refrigerant and the temperature of the air becomes gradually smaller. In the refrigerant flowing as the counter flow, a temperature difference between the temperature of the refrigerant and the temperature of the air can be ensured as compared with the case where the refrigerant flows as the parallel flow.
In the air conditioner 1 described above, by adjusting the outdoor 2 nd flow rate adjustment valve 25b, the flow rate of the refrigerant flowing through the outdoor 2 nd heat exchanger 15 as a parallel flow is reduced, and accordingly, the flow rate of the refrigerant flowing through the outdoor 1 st heat exchanger 13 can be increased.
Therefore, the temperature TBout of the refrigerant immediately after flowing through the outdoor 2 nd heat exchanger 15 is lower than that in the case where the outdoor 1 st flow rate adjustment valve 25a and the outdoor 2 nd flow rate adjustment valve 25b are not provided (see fig. 5). The temperature TAout of the refrigerant immediately after flowing through the outdoor 1 st heat exchanger 13 is higher than that in the case where the outdoor 1 st flow rate adjustment valve 25a and the outdoor 2 nd flow rate adjustment valve 25b are not provided (see fig. 5).
This means that the temperature difference between the temperature TAout and the temperature TBout can be reduced by the outdoor 2 nd flow rate adjustment valve 25b or the like. Therefore, by adjusting the flow rate of the refrigerant by the outdoor 2 nd flow rate adjustment valve 25b or the like, the temperature TAout (outlet side enthalpy) of the refrigerant immediately after flowing through the outdoor 1 st heat exchanger 13 and the temperature TBout (outlet side enthalpy) of the refrigerant immediately after flowing through the outdoor 2 nd heat exchanger 15 are made almost the same, and thereby the heat transfer performance as the outdoor heat exchanger 11 can be improved.
Next, a case of the heating operation will be described. Fig. 19 shows graphs GR1 and GR2 related to the temperature of the refrigerant flowing through the outdoor heat exchanger 11 and graphs GA1 and GA2 related to the temperature of the air passing through the outdoor heat exchanger 11 during the heating operation. The outdoor heat exchanger 11 and the like shown in fig. 17 are collectively shown at the upper layer.
As shown in fig. 19, a graph GR1 shows a relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 1 st heat exchanger 13. The temperature of the refrigerant immediately before flowing into the outdoor 1 st heat exchanger 13 is a temperature TAin, and the temperature of the refrigerant immediately after flowing through the outdoor 1 st heat exchanger 13 is a temperature TAout.
The graph GR2 shows the relationship between the flow (direction) of air and the temperature of the refrigerant flowing through the outdoor 2 nd heat exchanger 15. The temperature of the refrigerant immediately before flowing into the outdoor 2 nd heat exchanger 15 is a temperature TBin, and the temperature of the refrigerant immediately after flowing through the outdoor 2 nd heat exchanger 15 is a temperature TBout.
The graph GA1 shows the relationship between the flow (direction) of air and the temperature of air passing through the outdoor 1 st heat exchanger 13. The graph GA2 shows the relationship between the flow (direction) of air and the temperature of the air passing through the outdoor 2 nd heat exchanger 15.
As shown in the upper layer of fig. 19, in the outdoor 1 st heat exchanger 13, the refrigerant flows as parallel flows. In the outdoor 2 nd heat exchanger 15, the refrigerant flows as a counter flow.
On the other hand, as shown in graphs GA1 and GA2, the temperature of the air passing through the outdoor heat exchanger 11 increases by heat exchange with the refrigerant. Therefore, in the refrigerant flowing as the parallel flow, the temperature difference between the temperature of the refrigerant and the temperature of the air becomes gradually smaller. In the refrigerant flowing as the counter flow, a temperature difference between the temperature of the refrigerant and the temperature of the air can be ensured as compared with the case where the refrigerant flows as the parallel flow.
In the air conditioner 1 described above, by adjusting the outdoor 1 st flow rate adjustment valve 25a, the flow rate of the refrigerant flowing through the outdoor 1 st heat exchanger 13 as a parallel flow is reduced, and accordingly, the flow rate of the refrigerant flowing through the outdoor 2 nd heat exchanger 15 can be increased.
Therefore, the temperature TAout of the refrigerant immediately after flowing through the outdoor 1 st heat exchanger 13 is higher than that in the case where the outdoor 1 st flow rate adjustment valve 25a and the outdoor 2 nd flow rate adjustment valve 25b are not provided (see fig. 5). The temperature TBout of the refrigerant immediately after flowing through the outdoor 2 nd heat exchanger 15 is lower than that in the case where the outdoor 1 st flow rate adjustment valve 25a and the outdoor 2 nd flow rate adjustment valve 25b are not provided (see fig. 5).
This means that the temperature difference between the temperature TAout and the temperature TBout can be reduced by adjusting the outdoor 1 st flow rate adjustment valve 25a or the like. Therefore, by adjusting the flow rate of the refrigerant by the outdoor 1 st flow rate adjustment valve 25a or the like, the temperature TAout (outlet side enthalpy) of the refrigerant immediately after flowing through the outdoor 1 st heat exchanger 13 and the temperature TBout (outlet side enthalpy) of the refrigerant immediately after flowing through the outdoor 2 nd heat exchanger 15 are made to be substantially the same temperature (for example, the superheat is about 0.5 ℃), whereby the heat transfer performance as the outdoor heat exchanger 11 can be improved.
In order to measure the temperature of the refrigerant with high accuracy, a temperature sensor such as a thermistor may be provided in the refrigerant pipe 41.
As shown in fig. 15, in the outdoor 1 st heat exchanger 13, it is preferable that the temperature sensor T1 is provided at a portion S1 of the refrigerant piping 41, and the temperature sensor T2 is provided at a portion S2 of the refrigerant piping 41, wherein the portion S1 of the refrigerant piping 41 is located on the opposite side of the gas-liquid two-phase distributor 21a from the side where the 1 st portion 13a is connected, and the portion S2 of the refrigerant piping 41 is located on the opposite side of the gas distributor 23a from the side where the 2 nd portion 13b is connected.
In the outdoor 2 nd heat exchanger 15, it is preferable that the temperature sensor T4 is provided at the portion S4 of the refrigerant piping 41, and the temperature sensor T3 is provided at the portion S3 of the refrigerant piping 41, wherein the portion S4 of the refrigerant piping 41 is located on the opposite side of the gas-liquid two-phase distributor 21b from the side where the 4 th portion 15b is connected, and the portion S3 of the refrigerant piping 41 is located on the opposite side of the gas distributor 23b from the side where the 3 rd portion 15a is connected.
In addition to the temperature sensors T1 to T4, for example, pressure sensors may be provided in the refrigerant piping 41 (sections S1 to S4). By means of the pressure sensor, the enthalpy of each outlet side can be calculated more accurately.
The outdoor heat exchanger 11 and the like have been described as having a structure in which the 1 st portion 13a (3 rd portion 15 a) and the 2 nd portion 13b (4 th portion 15 b) are arranged in the ventilation direction and the number of heat transfer tubes is 2, but may have a multi-row structure of 3 or more rows. Further, as the heat transfer tube to be disposed in the outdoor heat exchanger 11 or the like, a round tube having a circular cross-sectional shape may be used, or a flat tube having a flat cross-sectional shape may be used.
In the air conditioner 1 of each embodiment, the operation and effect are described as represented by the outdoor heat exchanger 11 in the outdoor unit 3, but the same effect as the outdoor heat exchanger 11 can be obtained also for the indoor heat exchanger 27 in the indoor unit 5. Further, the 1 st heat exchanger and the 2 nd heat exchanger may be applied to at least one of the outdoor heat exchanger 11 and the indoor heat exchanger 27.
The air conditioner 1 described in each embodiment can be variously combined as necessary.
The embodiments disclosed herein are merely examples and are not limited by the embodiments. The disclosure is not to be seen as limited by the scope of the foregoing description, but is to be seen as set forth by the appended claims, which are intended to include all changes which come within the meaning and range of equivalency of the claims.
Industrial applicability
The present disclosure is effectively used in an air conditioner using a non-azeotropic mixed refrigerant as a refrigerant.
Description of the reference numerals
1 an air conditioner, 3 an outdoor unit, 5 an indoor unit, 7a compressor, 9 a four-way valve, 11 an outdoor heat exchanger, 13 an outdoor 1 st heat exchanger, 13a 1 st part, 13b 2 nd part, 21a GAs-liquid two-phase distributor, 23a GAs distributor, 15 an outdoor 2 nd heat exchanger, 15a 3 rd part, 15b 4 th part, 21b GAs-liquid two-phase distributor, 23b GAs distributor, 17 outdoor 3 rd heat exchanger, 17a 5 th part, 17b 6 th part, 21c GAs-liquid two-phase distributor, 23c GAs distributor, 19 expansion valve, 25a outdoor 1 st flow rate regulating valve, 25b outdoor 2 nd flow rate regulating valve, 27 indoor heat exchanger, a 29 room 1 st heat exchanger, a 33a GAs-liquid two-phase distributor, a 35a GAs distributor, a 31 room 2 nd heat exchanger, a 33b GAs-liquid two-phase distributor, a 35b GAs distributor, a 37a room 1 st flow rate adjustment valve, a 37b room 2 nd flow rate adjustment valve, 41 refrigerant piping, 43 zeotropic mixed refrigerant, a 51 refrigeration cycle circuit, 61 branching sections, P1, P2, P3, P4 branching and merging points, R1, R2, R3, R4, R5 flow paths, TAin, TAout, TBin, TBout, TCin, TCout temperatures, GR1, GR2, GR3, GA1, GA2, GA3 patterns, S1, S2, S3, S4 sections, T1, T2, T3, T4 temperature sensors, YA, YB arrows.

Claims (9)

1. An air conditioner is provided with a refrigeration cycle for circulating a non-azeotropic refrigerant mixture, wherein the refrigeration cycle comprises an outdoor unit and an indoor unit,
at least one of the outdoor unit and the indoor unit includes:
a 1 st heat exchanger comprising a 1 st section and a 2 nd section connected in series;
a 2 nd heat exchanger including a 3 rd section and a 4 th section connected in series;
a 1 st gas-liquid two-phase distributor connected to a side opposite to a side to which the 1 st part and the 2 nd part are connected;
a 1 st gas distributor connected to a side opposite to the side to which the 1 st part is connected with respect to the 2 nd part;
a 2 nd gas distributor connected to a side opposite to a side to which the 3 rd part is connected with the 4 th part;
a 2 nd gas-liquid two-phase distributor connected to a side opposite to a side to which the 4 th portion and the 3 rd portion are connected;
a 1 st flow path including a portion connecting the 1 st gas distributor, the 2 nd portion, the 1 st portion, and the 1 st gas-liquid two-phase distributor in this order; and
a 2 nd flow path including a portion connecting the 2 nd gas distributor, the 3 rd portion, the 4 th portion, and the 2 nd gas-liquid two-phase distributor in this order,
The 1 st flow path provided with the 1 st heat exchanger and the 2 nd flow path provided with the 2 nd heat exchanger are connected in parallel to the refrigeration cycle circuit so as to connect the 1 st gas-liquid two-phase distributor and the 2 nd gas-liquid two-phase distributor and to connect the 1 st gas distributor and the 2 nd gas distributor,
the air conditioner has a 1 st operation mode in which the 1 st heat exchanger and the 2 nd heat exchanger function as a condenser, and a 2 nd operation mode in which the 1 st heat exchanger and the 2 nd heat exchanger function as an evaporator,
in the ventilation direction of the air passing through the 1 st heat exchanger and the 2 nd heat exchanger respectively,
the 1 st part is arranged on the windward side,
the 2 nd part is arranged on the leeward side,
the 3 rd part is arranged on the windward side,
the 4 th portion is disposed on the leeward side.
2. The air conditioner according to claim 1, wherein,
in the case of the 1 st operation mode,
in the 1 st flow path, the zeotropic refrigerant mixture is a counter flow which flows in the order of the 1 st gas distributor, the 2 nd part arranged on the leeward side, the 1 st part arranged on the windward side, and the 1 st gas-liquid two-phase distributor,
In the 2 nd flow path, the zeotropic refrigerant mixture is a parallel flow in which the 2 nd gas distributor, the 3 rd part arranged on the windward side, the 4 th part arranged on the leeward side, and the 2 nd gas-liquid two-phase distributor flow in this order.
3. The air conditioner according to claim 1 or 2, wherein,
in the case of the 2 nd operation mode,
in the 1 st flow path, the zeotropic refrigerant mixture is formed into parallel flow which flows in sequence through the 1 st gas-liquid two-phase distributor, the 1 st part arranged on the windward side, the 2 nd part arranged on the leeward side and the 1 st gas distributor,
in the 2 nd flow path, the zeotropic refrigerant mixture is a counter flow which flows in the 2 nd gas-liquid two-phase distributor, the 4 th part arranged on the leeward side, the 3 rd part arranged on the windward side, and the 2 nd gas distributor in order.
4. An air conditioner according to claim 2 or 3, wherein,
the air conditioner is provided with:
a 3 rd heat exchanger comprising a 5 th section and a 6 th section connected in series;
a 3 rd gas-liquid two-phase distributor connected to a side opposite to a side to which the 5 th portion and the 6 th portion are connected;
A 3 rd gas distributor connected to a side opposite to a side to which the 6 th portion is connected with the 5 th portion;
a 3 rd flow path including a portion connecting the 3 rd gas-liquid two-phase distributor, the 5 th portion, the 6 th portion, and the 3 rd gas distributor in this order; and
an expansion valve disposed between the outdoor unit and the indoor unit in the refrigeration cycle,
the 3 rd flow path in which the 3 rd heat exchanger is arranged is connected in series between the expansion valve and the 1 st flow path and the 2 nd flow path connected in parallel,
in the ventilation direction of the air passing through the 3 rd heat exchanger,
the 5 th part is arranged on the windward side,
the 6 th part is arranged on the leeward side,
the number of refrigerant channels in the 1 st heat exchanger through which the zeotropic refrigerant mixture flows is the 1 st refrigerant channel number,
the number of refrigerant channels in the 2 nd heat exchanger through which the zeotropic refrigerant mixture flows is the 2 nd refrigerant channel number,
the number of refrigerant channels in the 3 rd heat exchanger through which the zeotropic refrigerant mixture flows is the 3 rd refrigerant channel number,
the 3 rd refrigerant flow path number is smaller than the 1 st refrigerant flow path number and the 2 nd refrigerant flow path number,
The 3 rd heat exchanger is disposed below the 1 st heat exchanger and the 2 nd heat exchanger.
5. The air conditioner according to claim 4, wherein,
in the case of the 1 st operation mode, the zeotropic refrigerant mixture flows from the 1 st flow path and the 2 nd flow path connected in parallel to the 3 rd flow path,
in the 3 rd flow path, the zeotropic refrigerant mixture is a counter flow which flows in the order of the 3 rd gas distributor, the 6 th part, the 5 th part, and the 3 rd gas-liquid two-phase distributor.
6. The air conditioner according to claim 4 or 5, wherein,
in the case of the 2 nd operation mode, the zeotropic refrigerant mixture flows from the 3 rd flow path to the 1 st flow path and the 2 nd flow path which are connected in parallel,
in the 3 rd flow path, the zeotropic refrigerant mixture is formed as parallel flow which flows in the 3 rd gas-liquid two-phase distributor, the 5 th part, the 6 th part and the 3 rd gas distributor in order.
7. The air conditioner according to any one of claims 1 to 6, wherein,
the air conditioner is provided with:
a 1 st flow rate adjustment valve disposed in a portion of the 1 st flow path, the portion of the 1 st flow path being located on a side opposite to a side to which the 1 st gas-liquid two-phase distributor is connected;
And a 2 nd flow rate adjustment valve disposed in a portion of the 2 nd flow path, the portion of the 2 nd flow path being located on a side opposite to a side to which the 4 th portion is connected with respect to the 2 nd gas-liquid two-phase distributor.
8. The air conditioner according to claim 7, wherein,
any one of a temperature sensor for measuring the temperature of the zeotropic refrigerant mixture and a pressure sensor for measuring the pressure of the zeotropic refrigerant mixture is provided separately from the other:
the 1 st flow path is located on the opposite side of the 1 st gas-liquid two-phase distributor from the side to which the 1 st part is connected;
the 1 st flow path is located on the opposite side of the 1 st gas distributor from the side to which the 2 nd part is connected;
the 2 nd flow path is located on the opposite side of the 2 nd gas-liquid two-phase distributor from the side to which the 4 th portion is connected; and
the 2 nd flow path is located on the opposite side of the 2 nd gas distributor from the side to which the 3 rd section is connected.
9. The air conditioner according to any one of claims 1 to 8, wherein,
at a position where the 1 st flow path and the 2 nd flow path are connected in parallel to the refrigeration cycle, any one of a T-shaped branching portion and a Y-shaped branching portion is arranged.
CN202180097177.6A 2021-04-23 2021-04-23 Air conditioner Pending CN117203476A (en)

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Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08170864A (en) 1994-12-19 1996-07-02 Sanyo Electric Co Ltd Heat pump air conditioning apparatus and defrosting method
JPH09196489A (en) 1996-01-19 1997-07-31 Fujitsu General Ltd Refrigeration cycle for air conditioner
JP2010139097A (en) * 2008-12-09 2010-06-24 Mitsubishi Electric Corp Air conditioner
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WO2018047331A1 (en) * 2016-09-12 2018-03-15 三菱電機株式会社 Air conditioning device
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WO2019003385A1 (en) * 2017-06-29 2019-01-03 三菱電機株式会社 Outdoor unit and refrigeration cycle device
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