CN210772853U - Heat exchanger and refrigeration cycle device - Google Patents
Heat exchanger and refrigeration cycle device Download PDFInfo
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- CN210772853U CN210772853U CN201890000435.8U CN201890000435U CN210772853U CN 210772853 U CN210772853 U CN 210772853U CN 201890000435 U CN201890000435 U CN 201890000435U CN 210772853 U CN210772853 U CN 210772853U
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- heat exchanger
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- 238000005057 refrigeration Methods 0.000 title claims description 22
- 230000007246 mechanism Effects 0.000 claims abstract description 89
- 239000012530 fluid Substances 0.000 claims abstract description 57
- 238000002360 preparation method Methods 0.000 claims 2
- 239000003507 refrigerant Substances 0.000 description 209
- 238000001816 cooling Methods 0.000 description 40
- 238000010438 heat treatment Methods 0.000 description 36
- 239000007788 liquid Substances 0.000 description 29
- 230000004048 modification Effects 0.000 description 7
- 238000012986 modification Methods 0.000 description 7
- 239000007787 solid Substances 0.000 description 7
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000010792 warming Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 1
- 239000000758 substrate Substances 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
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- 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
The utility model discloses a heat exchanger possesses main heat exchange portion, at least one 1 st supplementary heat exchange portion, will introduce into the working fluid of main heat exchange portion and distribute the distributor of a plurality of routes, set up in the 1 st valve mechanism of header and set up in the 1 st piping that the working fluid flows in and flows out and the 2 nd valve mechanism between main heat exchange portion and the 1 st supplementary heat exchange portion. The 1 st auxiliary heat exchange portion has a smaller number of heat transfer pipes than the main heat exchange portion, and is formed with a smaller number of routes of the working fluid than the main heat exchange portion. The 1 st valve mechanism is provided in the header between the main region of the heat transfer pipe connected to the main heat exchange portion and the auxiliary region of the heat transfer pipe connected to the 1 st auxiliary heat exchange portion, and allows the flow of the working fluid only in the direction from the auxiliary region toward the main region. The 2 nd valve mechanism permits the flow of the working fluid flowing in from the 1 st pipe only in a direction from the 1 st pipe toward the side where the distributor and the 1 st auxiliary heat exchange portion are arranged.
Description
Technical Field
The present invention relates to a heat exchanger and a refrigeration cycle apparatus having the same, and more particularly, to a change in a route structure of a working fluid in the heat exchanger.
Background
Conventionally, some refrigeration cycle devices include a heat source side unit and a load side unit. For example, the heat source side unit includes a compressor, a heat source side heat exchanger, and a four-way valve, and the load side unit includes a load side heat exchanger. The compressor, the heat source side heat exchanger, the four-way valve, and the load side heat exchanger are connected by pipes to form a refrigerant circuit in which a refrigerant circulates in the pipes. By controlling the four-way valve, the flow direction of the refrigerant in the refrigerant circuit is switched, and the heating operation and the cooling operation of the refrigeration cycle device are switched.
Patent document 1: japanese laid-open patent publication No. 2012-107857
However, in the air conditioner of patent document 1, in switching between cooling and heating, it is necessary to interlock the operation of the four-way valve and the opening and closing of the various valves. Therefore, there is a problem that the control of the control device becomes complicated and the substrate structure mounted on the control device becomes complicated.
Disclosure of Invention
The present invention has been made to solve the above problems, and an object of the present invention is to provide a heat exchanger and a refrigeration cycle apparatus that realize a refrigerant route structure in a cooling operation and a heating operation with a simple structure.
The heat exchanger of the present invention includes a heat transfer pipe through which a working fluid flows and a header connected to the heat transfer pipe, and exchanges heat between the working fluid and a gas, and includes: a main heat exchange unit having a plurality of heat transfer tubes and formed with a plurality of routes for the working fluid; at least one 1 st auxiliary heat exchange unit having a smaller number of heat transfer tubes than the main heat exchange unit and having a smaller number of routes for the working fluid than the main heat exchange unit; a distributor that distributes the working fluid introduced into the main heat exchanger to a plurality of routes; a 1 st valve mechanism that is provided in the header between a main region connected to the heat transfer tubes of the main heat exchange portion and an auxiliary region connected to the heat transfer tubes of the 1 st auxiliary heat exchange portion, and allows the flow of the working fluid only in a direction from the auxiliary region toward the main region; and a 2 nd valve mechanism which is provided between a 1 st pipe into which the working fluid flows and from which the working fluid flows, and the main heat exchange unit and the 1 st auxiliary heat exchange unit, and permits the flow of the working fluid flowing in from the 1 st pipe only in a direction from the 1 st pipe toward a side where the distributor and the 1 st auxiliary heat exchange unit are arranged.
Preferably, the 1 st pipe is connected to the header, and the 1 st pipe is provided with a 3 rd valve mechanism, the 3 rd valve mechanism preventing the working fluid flowing in from the 1 st pipe from flowing into the header and allowing only the working fluid flowing out from the header to flow out from the 1 st pipe.
Preferably, a 2 nd auxiliary heat exchange unit is provided between the header and the 1 st pipe, and the 2 nd auxiliary heat exchange unit has a smaller number of the heat transfer tubes than the main heat exchange unit, and has a smaller number of the paths of the working fluid than the main heat exchange unit.
Preferably, the 2 nd valve mechanism is a three-way valve configured to switch a path of communication according to a pressure difference between the working fluid flowing into the heat exchanger and the working fluid flowing out of the heat exchanger.
Preferably, the three-way valve includes: 1 st valve port connected with the collecting pipe; a 2 nd port connected to the 1 st pipe; a 3 rd valve port connected to the distributor and the 1 st auxiliary heat exchange unit; and a movable mechanism unit that switches opening and closing of the 1 st port, the 2 nd port, and the 3 rd port in accordance with a pressure difference between the working fluid flowing into the heat exchanger and the working fluid flowing out of the heat exchanger.
Preferably, the movable mechanism portion switches opening and closing of the 1 st port, the 2 nd port, and the 3 rd port in accordance with a pressure difference between the working fluid flowing through the 2 nd pipe and the working fluid flowing through the 1 st pipe, the 2 nd pipe is connected to the header, and the working fluid flows into and out of the 2 nd pipe in a direction opposite to a direction in which the working fluid flows into and out of the 1 st pipe.
Preferably, the movable mechanism portion communicates the 1 st port with the 2 nd port when the working fluid flows in from the 2 nd pipe and flows out from the 1 st pipe, and communicates the 2 nd port with the 3 rd port when the working fluid flows in from the 1 st pipe and flows out from the 2 nd pipe.
Preferably, the 1 st valve mechanism is a check valve.
Preferably, the 2 nd valve mechanism is a check valve.
Preferably, the 3 rd valve mechanism is a check valve.
Preferably, the heat exchanger includes a plurality of the 1 st auxiliary heat exchange units.
The refrigeration cycle apparatus according to the present invention includes such a heat exchanger.
In addition, the present invention relates to a refrigeration cycle apparatus, which includes: an outdoor unit having a compressor and the heat exchanger; and an indoor unit having an indoor heat exchanger, wherein the three-way valve is configured to switch a path communicated with the compressor based on a pressure difference between the working fluid on a suction side of the compressor and the working fluid on a discharge side of the compressor.
According to the heat exchanger and the refrigeration cycle apparatus of the present invention, since the 1 st valve mechanism and the 2 nd valve mechanism which allow the flow of the working fluid only in one direction are provided, routes having different structures are formed in accordance with the direction of the flow of the working fluid flowing into the heat exchanger. Therefore, when the path of the working fluid flowing in different directions during the cooling operation and the heating operation is configured, the control of the control device is not necessary, and the control of the control device and the complexity of the board of the control device can be suppressed.
Drawings
Fig. 1 is a configuration diagram of a refrigeration cycle apparatus according to embodiment 1 of the present invention.
Fig. 2 is a view schematically showing the structure of an outdoor heat exchanger according to embodiment 1 of the present invention.
Fig. 3 is a view schematically showing the structure of an outdoor heat exchanger according to a modification of embodiment 1 of the present invention.
Fig. 4 is a view schematically showing the structure of an outdoor heat exchanger according to embodiment 2 of the present invention.
Fig. 5 is a view schematically showing the structure of an outdoor heat exchanger according to embodiment 3 of the present invention.
Fig. 6 is a diagram schematically showing the configuration around the outdoor heat exchanger in the outdoor unit of the refrigeration cycle apparatus according to embodiment 4 of the present invention.
Detailed Description
Hereinafter, embodiments of a heat exchanger and a refrigeration cycle apparatus according to the present invention will be described in detail with reference to the drawings. The present invention is not limited to the embodiments described below. In the following drawings, the size and shape of each component may be different from those of an actual apparatus.
Fig. 1 is a configuration diagram of a refrigeration cycle apparatus according to embodiment 1 of the present invention. The refrigeration cycle apparatus 1 includes an outdoor unit 10 as a heat source side unit and an indoor unit 20 as a load side unit. The outdoor unit 10 and the indoor unit 20 are connected via a gas refrigerant pipe 31 and a liquid refrigerant pipe 32. The outdoor unit 10 includes a compressor 11, a flow path switching unit 12, an outdoor heat exchanger 13 as a heat source side heat exchanger, a 1 st expansion valve 14, a 2 nd expansion valve 15, and a refrigerant container 16. The indoor unit 20 has an indoor heat exchanger 21 as a load-side heat exchanger. The refrigerant circuit 30 is formed by the compressor 11, the flow path switching unit 12, the outdoor heat exchanger 13, the 1 st expansion valve 14, the 2 nd expansion valve 15, the refrigerant container 16, the indoor heat exchanger 21, and refrigerant pipes including the gas refrigerant pipe 31 and the liquid refrigerant pipe 32 described above. A refrigerant as a working fluid circulates in the refrigerant circuit.
The compressor 11 sucks the refrigerant, compresses the sucked refrigerant, and brings the refrigerant into a high-temperature and high-pressure state. For example, the operation frequency is arbitrarily changed by an inverter circuit or the like, thereby changing the capacity of the compressor 11, that is, the amount of refrigerant to be delivered per unit time.
The flow switching unit 12 switches the flow of the refrigerant in the refrigerant circuit 30, and is, for example, a four-way valve. The flow path switching unit 12 is controlled by a control device not shown.
The outdoor heat exchanger 13 exchanges heat between the refrigerant and the outdoor air, i.e., gas, and functions as a condenser during the cooling operation and as an evaporator during the heating operation. Outdoor air is supplied to the outdoor heat exchanger 13 by a fan not shown.
The 1 st expansion valve 14 and the 2 nd expansion valve 15 are valves for decompressing the refrigerant flowing through the refrigerant circuit 30, and are electronic expansion valves capable of adjusting the opening degree. The refrigerant container 16 is provided between the 1 st expansion valve 14 and the 2 nd expansion valve 15, and is an excess refrigerant storage container that stores excess refrigerant.
The indoor heat exchanger 21 exchanges heat between the refrigerant and the indoor air, i.e., gas, and functions as an evaporator during the cooling operation and as a condenser during the heating operation. Indoor air is supplied to the indoor heat exchanger 21 by a fan not shown.
In fig. 1, solid arrows indicate the flow of the refrigerant during the cooling operation, and broken arrows indicate the flow of the refrigerant during the heating operation. During the cooling operation, the flow path switching unit 12 is switched to a state indicated by a solid arrow by a control device, not shown. In the cooling operation, when a high-temperature and high-pressure gas refrigerant is discharged from the compressor 11, the gas refrigerant is introduced into the outdoor heat exchanger 13 via the flow path switching unit 12. In the outdoor heat exchanger 13, the gas refrigerant is condensed by heat exchange with outdoor air, and becomes a liquid refrigerant. The liquid refrigerant flowing out of the outdoor heat exchanger 13 is introduced into the 1 st expansion valve 14. The liquid refrigerant is decompressed by the 1 st expansion valve 14 to become a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state passes through the refrigerant container 16, passes through the 2 nd expansion valve 15, and is introduced into the indoor heat exchanger 21 through the liquid refrigerant pipe 32. In the indoor heat exchanger 21, the refrigerant exchanges heat with the indoor air, evaporates, and turns into a low-pressure gas refrigerant. The low-pressure gas refrigerant flowing out of the indoor heat exchanger 21 is introduced into the flow switching unit 12 through the gas refrigerant pipe 31. The low-pressure gas refrigerant is sucked into the compressor 11 through the flow switching unit 12.
During the heating operation, the flow switching unit 12 is switched to a state indicated by a broken-line arrow by a control device, not shown. In the heating operation, when a high-temperature and high-pressure gas refrigerant is discharged from the compressor 11, the gas refrigerant is introduced into the indoor heat exchanger 21 through the flow switching unit 12 and the gas refrigerant pipe 31. In the indoor heat exchanger 21, the gas refrigerant is condensed by heat exchange with the indoor air, and becomes a liquid refrigerant. The liquid refrigerant flowing out of the indoor heat exchanger 21 is introduced into the 2 nd expansion valve 15 through the liquid refrigerant pipe 32. The liquid refrigerant is decompressed by the 2 nd expansion valve 15 to become a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state passes through the refrigerant container 16, passes through the 1 st expansion valve 14, and is introduced into the outdoor heat exchanger 13. In the outdoor heat exchanger 13, the refrigerant exchanges heat with outdoor air, evaporates, and turns into a gas refrigerant. The gas refrigerant flowing out of the outdoor heat exchanger 13 is sucked into the compressor 11 through the flow switching unit 12.
Fig. 2 is a view schematically showing the structure of an outdoor heat exchanger according to embodiment 1 of the present invention. In fig. 2, solid arrows indicate the flow of the refrigerant during the cooling operation, and broken arrows indicate the flow of the refrigerant during the heating operation.
The outdoor heat exchanger 13 is connected to a 1 st pipe 41 and a 2 nd pipe 42. The 1 st pipe 41 is connected to the 1 st expansion valve 14 shown in fig. 1. The 2 nd pipe 42 is connected to the flow path switching unit 12 shown in fig. 1. During the cooling operation, the refrigerant flows into the outdoor heat exchanger 13, which operates as a condenser, from the 2 nd pipe 42, and flows out from the 1 st pipe 41. During the heating operation, the refrigerant flows into the outdoor heat exchanger 13, which operates as an evaporator, from the 1 st pipe 41, and the refrigerant flows out from the 2 nd pipe 42. The direction of inflow and outflow of the refrigerant in the 1 st pipe 41 and the direction of inflow and outflow of the refrigerant in the 2 nd pipe 42 are opposite to each other during the cooling operation and the heating operation.
The outdoor heat exchanger 13 includes a main heat exchange portion 50, a 1 st auxiliary heat exchange portion 51, a header 53, and a distributor 54. The outdoor heat exchanger 13 is, for example, a fin-and-tube heat exchanger, the main heat exchange portion 50 has a plurality of heat transfer tubes 150, and the 1 st auxiliary heat exchange portion 51 has a smaller number of heat transfer tubes 151 than the number of heat transfer tubes 150 of the main heat exchange portion 50. The main heat exchange portion 50 and the 1 st auxiliary heat exchange portion 51 have fins not shown. In the main heat exchange portion 50 and the 1 st auxiliary heat exchange portion 51, a plurality of heat transfer tubes are arranged in parallel in the vertical direction, and a plurality of fins are inserted perpendicularly to the plurality of heat transfer tubes arranged in parallel. The 1 st auxiliary heat exchange unit 51 is disposed below the main heat exchange unit 50, and the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51 are disposed along the vertical direction.
A plurality of routes of the refrigerant are formed inside the heat transfer pipe 150 of the main heat exchange portion 50 and the heat transfer pipe 151 of the 1 st auxiliary heat exchange portion 51. The number of the 1 st auxiliary heat exchange part 51 is smaller than that of the main heat exchange part 50. In fig. 2, 4 heat transfer pipes 150 are shown for the main heat exchanger 50 and 1 heat transfer pipe 151 is shown for the 1 st auxiliary heat exchanger 51, but the number of heat transfer pipes and the number of routes are not specified, but the route structure is conceptually shown. Further, the total number of heat transfer pipes is determined based on the design of the outdoor heat exchanger 13, and the total number of routes is determined according to the total number of heat transfer pipes. The outdoor heat exchanger 13 is configured such that the number of heat transfer tubes 151 of the 1 st auxiliary heat exchange portion 51 is smaller than the number of heat transfer tubes 150 of the main heat exchange portion 50 in the total number of heat transfer tubes. Also, the outdoor heat exchanger 13 is configured such that the number of passes of the 1 st auxiliary heat exchange portion 51 is smaller than the number of passes of the main heat exchange portion 50 in the total number of passes determined according to the total number of heat transfer tubes.
The header 53 is connected to the 1 st pipe 41 and the 2 nd pipe 42. The header 53 has a main region 53A connected to the heat transfer tubes 150 of the main heat exchange unit 50, and an auxiliary region 53B connected to the heat transfer tubes 151 of the 1 st auxiliary heat exchange unit 51.
The distributor 54 has one end connected to the main heat exchange unit 50 and the other end connected to the 1 st auxiliary heat exchange unit 51. In the heating operation, the refrigerant is distributed to a plurality of routes by the distributor 54 and introduced into the main heat exchange unit 50. During cooling operation, the refrigerant flowing out of the main heat exchange portion 50 into a plurality of paths is merged in the distributor 54.
At the 1 st branch point P1, the 3 rd pipe 43 branches off from the 1 st pipe 41, and the 3 rd pipe 43 extends toward the side where the distributor 54 is located. At the 2 nd branch point P2, a 4 th pipe 44 connected to the 1 st auxiliary heat exchange unit 51 and a 5 th pipe 45 connected to the distributor 54 branch off from the 3 rd pipe 43.
The header 53 is provided with a 1 st valve mechanism 61 between the main area 53A and the sub area 53B. The 1 st valve mechanism 61 is, for example, a check valve, and allows the flow of the refrigerant only in the direction from the auxiliary area 53B toward the main area 53A.
The 4 th pipe 44 is provided with a 2 nd valve mechanism 62 between the 1 st branch point P1 and the 2 nd branch point P2. The 2 nd valve mechanism 62 is, for example, a check valve, and allows the flow of the refrigerant only in the direction from the 1 st branch point P1 toward the 2 nd branch point P2. That is, the 2 nd valve mechanism 62 allows the flow of the refrigerant flowing from the 1 st pipe 41 only in the direction from the 1 st pipe 41 toward the side where the distributor 54 and the 1 st auxiliary heat exchange unit 51 are arranged.
The 3 rd pipe 43 is provided with a 3 rd valve mechanism 63. The 3 rd valve mechanism 63 is, for example, a check valve, and allows the flow of the refrigerant only in the direction from the header 53 toward the 1 st branch point P1. That is, the 3 rd valve mechanism 63 prevents the refrigerant flowing in from the 1 st pipe 41 from flowing into the header 53, and allows only the refrigerant flowing out of the header 53 to flow out from the 1 st pipe 41.
When the refrigeration cycle apparatus 1 of fig. 1 performs a cooling operation, the high-temperature, high-pressure gas refrigerant compressed and discharged by the compressor 11 flows into the main region 53A of the header 53 via the 2 nd pipe 42. Since the header 53 is provided with the 1 st valve mechanism 61, the gas refrigerant flowing into the header 53 is introduced only into the main heat exchange portion 50 without flowing from the main area 53A into the auxiliary area 53B. The gas refrigerant is condensed by heat exchange with the outdoor air in the main heat exchange portion 50, and becomes a gas-liquid two-phase state. The refrigerant in the gas-liquid two-phase state is introduced into the distributor 54 while being divided into a plurality of routes, and merges in the distributor 54. A 2 nd valve mechanism 62 is provided on the downstream side of the distributor 54. Therefore, the refrigerant in the gas-liquid two-phase state is introduced into only the 1 st auxiliary heat exchange unit 51 without flowing from the 2 nd branch point P2 to the 1 st branch point P1. The refrigerant in the gas-liquid two-phase state further exchanges heat with the outdoor air in the 1 st auxiliary heat exchange portion 51. The refrigerant flowing out of the 1 st auxiliary heat exchange portion 51 flows into the auxiliary area 53B of the header 53. At this time, a pressure difference is generated between the upstream and downstream of the 1 st valve mechanism 61 at the time of the cooling operation, that is, between the main area 53A and the auxiliary area 53B, due to pressure loss in the main heat exchange portion 50 and the 1 st auxiliary heat exchange portion 51. Therefore, the refrigerant flowing out of the 1 st auxiliary heat exchange unit 51 and flowing into the auxiliary area 53B of the header 53 is not introduced into the main area 53A by the 1 st valve mechanism 61, but flows out of the header 53 and is introduced into the 1 st pipe 41. Since the 3 rd valve mechanism 63 of the 1 st pipe 41 is a valve that allows the refrigerant to flow from the header 53 in the direction toward the 1 st branch point P1, the refrigerant introduced into the 1 st pipe 41 flows out of the outdoor heat exchanger 13 via the 1 st pipe 41.
In this way, the arrangement of the 1 st valve mechanism 61, the 2 nd valve mechanism 62, and the 3 rd valve mechanism 63 allows the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51 to be connected in series in accordance with the flow direction of the refrigerant during the cooling operation of the refrigeration cycle apparatus 1. That is, the route of the main heat exchange unit 50 and the route of the 1 st auxiliary heat exchange unit 51 are connected in series during the cooling operation. Also, the number of routes of the 1 st auxiliary heat exchange part 51 is smaller than the number of routes of the main heat exchange part 50. Therefore, when the refrigerant flowing out of the main heat exchange portion 50 passes through the 1 st auxiliary heat exchange portion 51 via the distributor 54, the flow velocity of the refrigerant increases. As a result, high heat transfer efficiency can be obtained as the condenser.
When the refrigeration cycle apparatus 1 of fig. 1 performs a heating operation, the liquid refrigerant that exchanges heat with indoor air and is condensed in the indoor heat exchanger 21 flows through the 1 st expansion valve 14, the refrigerant container 16, and the 2 nd expansion valve 15, and flows into the outdoor heat exchanger 13 through the 1 st pipe 41. The 2 nd valve mechanism 62 is provided in the 3 rd pipe 43 branched at the 1 st branch point P1 and extending toward the distributor 54, and the 3 rd valve mechanism 63 is provided in the 1 st pipe 41 connected to the header 53. As described above, the 2 nd valve mechanism 62 of the 3 rd pipe 43 permits the flow of the refrigerant only in the direction from the 1 st branch point P1 toward the 2 nd branch point P2, and the 3 rd valve mechanism 63 of the 1 st pipe 41 prevents the refrigerant flowing in from the 1 st pipe 41 from flowing into the header 53. Therefore, the refrigerant flowing in from the 1 st pipe 41 is introduced into the side where the 1 st auxiliary heat exchange unit 51 and the distributor 54 are located, not into the header 53. The refrigerant is branched at a 2 nd branch point P2 and introduced into the distributor 54 and the 1 st auxiliary heat exchanger 51.
The refrigerant introduced into the 1 st auxiliary heat exchange unit 51 exchanges heat with outdoor air and is introduced into the auxiliary area 53B of the header 53. On the other hand, the refrigerant flowing into the distributor 54 is distributed to a plurality of routes by the distributor 54 and introduced into the main heat exchange portion 50. The refrigerant introduced into the main heat exchange unit 50 exchanges heat with outdoor air in the main heat exchange unit 50, and is introduced into the main region 53A of the header 53. At this time, no pressure difference is generated between the main area 53A and the auxiliary area 53B. Further, the 1 st valve mechanism 61 provided between the main area 53A and the auxiliary area 53B allows the flow of the refrigerant only in the direction from the auxiliary area 53B toward the main area 53A. Therefore, the refrigerant introduced into the auxiliary area 53B flows into the main area 53A, and merges with the refrigerant flowing from the main heat exchange unit 50 in the main area 53A. The refrigerant merged in the main region 53A flows out of the outdoor heat exchanger 13 through the 1 st pipe 41.
In this way, the arrangement of the 1 st valve mechanism 61, the 2 nd valve mechanism 62, and the 3 rd valve mechanism 63 allows the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51 to be connected in parallel in accordance with the flow direction of the refrigerant during the heating operation of the refrigeration cycle apparatus 1. That is, the route of the main heat exchange unit 50 and the route of the 1 st auxiliary heat exchange unit 51 are configured to be connected in parallel during the heating operation. Therefore, the refrigerant in a low-pressure liquid state is distributed to both the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51 as a whole. As a result, a decrease in the flow velocity of the refrigerant in the route of the main heat exchange portion 50 and the route of the 1 st auxiliary heat exchange portion 51 can be suppressed, and occurrence of pressure loss can be suppressed, and a decrease in efficiency when the outdoor heat exchanger 13 functions as an evaporator can be suppressed.
As described above, according to embodiment 1, the 1 st valve mechanism 61, the 2 nd valve mechanism 62, and the 3 rd valve mechanism 63 that allow the flow of the refrigerant only in one direction are provided on the refrigerant path of the outdoor heat exchanger 13. Therefore, the route structures corresponding to the flow of the refrigerant during the cooling operation and the flow of the refrigerant during the heating operation are formed. In addition, in the switching of cooling and heating, the route configuration of the refrigerant can be switched without controlling the opening and closing of an electromagnetic valve or the like by a control device. As described above, according to embodiment 1, the control of the control device and the board of the control device are not complicated, and the refrigerant can be made to flow through the route structures suitable for the cooling operation and the heating operation, respectively.
Fig. 3 is a view schematically showing the structure of an outdoor heat exchanger according to a modification of embodiment 1 of the present invention. In fig. 3, the same reference numerals are given to the same components as those shown in fig. 2. In fig. 3, solid arrows indicate the flow of the refrigerant during the cooling operation, and broken arrows indicate the flow of the refrigerant during the heating operation. In the present modification, 21 st auxiliary heat exchange units 51 are stacked below the main heat exchange unit 50, and the heat transfer tubes 151 of each of the 21 st auxiliary heat exchange units 51 are connected to the auxiliary region 53B of the header 53. At the 3 rd branch point P3, the 5 th pipe 45 branches into a 6 th pipe 46 connected to one of the 1 st auxiliary heat exchange units 51 and a 7 th pipe 47 connected to the distributor 54. The other structure is the same as the structure described in fig. 2.
As described above, the total number of routes is determined from the total number of heat transfer pipes determined based on the design of the outdoor heat exchanger 13. The outdoor heat exchanger 13 is configured such that the number of heat transfer tubes 151 of each of the 21 st auxiliary heat exchange portions 51 is smaller than the number of heat transfer tubes 150 of the main heat exchange portion 50, out of the total number of heat transfer tubes. That is, the outdoor heat exchanger 13 is configured such that the number of routes of the 21 st auxiliary heat exchange portions 51 is smaller than the number of routes of the main heat exchange portion 50 among the total number of routes determined according to the total number of heat transfer pipes.
In this modification, the 1 st valve mechanism 61, the 2 nd valve mechanism 62, and the 3 rd valve mechanism 63 that allow the flow of the refrigerant only in one direction are also provided on the route of the refrigerant in the outdoor heat exchanger 13. Therefore, the same effects as those described above can be obtained.
In this modification, 21 st auxiliary heat exchange units 51 are arranged vertically, but the number of 1 st auxiliary heat exchange units 51 is not limited to this. The number of the 1 st auxiliary heat exchange units 51 may be set to 3 or more within a design allowable range of the outdoor heat exchanger 13.
Fig. 4 is a view schematically showing the structure of an outdoor heat exchanger according to embodiment 2 of the present invention. In fig. 4, the same reference numerals are given to the same structural components as those in fig. 2 and 3. In fig. 4, solid arrows indicate the flow of the refrigerant during the cooling operation, and broken arrows indicate the flow of the refrigerant during the heating operation. The outdoor heat exchanger 100 according to embodiment 2 is provided with a 2 nd auxiliary heat exchange unit 52 in place of the 3 rd valve mechanism 63 according to embodiment 1. The 2 nd auxiliary heat exchanger 52 has a smaller number of heat transfer tubes 152 than the heat transfer tubes 150 of the main heat exchanger 50, and has fins, which are not shown, as in the 1 st auxiliary heat exchanger 51. The 2 nd auxiliary heat exchange unit 52 is disposed below the 1 st auxiliary heat exchange unit 51. That is, the main heat exchange unit 50, the 1 st auxiliary heat exchange unit 51, and the 2 nd auxiliary heat exchange unit 52 are disposed along the vertical direction. The other structure is the same as embodiment 1.
In the cooling operation, as in embodiment 1, the high-temperature and high-pressure gas refrigerant flows from the 2 nd pipe 42 into the main region 53A of the header 53, is introduced into the main heat exchange unit 50, is condensed into a gas-liquid two-phase state in the main heat exchange unit 50, and is introduced into the 1 st auxiliary heat exchange unit 51 through the distributor 54. That is, the gas refrigerant does not flow into the auxiliary area 53B by the 1 st valve mechanism 61. The refrigerant in the gas-liquid two-phase state does not flow from the 2 nd branch point P2 to the 1 st branch point P1 by the 2 nd valve mechanism 62. The refrigerant in a gas-liquid two-phase state that exchanges heat with outdoor air in the 1 st auxiliary heat exchange portion 51 and flows out of the 1 st auxiliary heat exchange portion 51 flows into the auxiliary area 53B of the header 53, and then flows into the 2 nd auxiliary heat exchange portion 52. The refrigerant in the gas-liquid two-phase state further exchanges heat with the outdoor air in the 2 nd auxiliary heat exchange portion 52, and flows out of the 2 nd auxiliary heat exchange portion 52. At this time, a pressure difference occurs between the upstream and downstream of the 2 nd valve mechanism 62 during the cooling operation due to the pressure loss in the 1 st auxiliary heat exchange portion 51 and the 2 nd auxiliary heat exchange portion 52. Therefore, the refrigerant that has flowed out of the 2 nd auxiliary heat exchange unit 52 and introduced into the 1 st pipe 41 does not flow to the side where the 1 st auxiliary heat exchange unit 51 and the distributor 54 are disposed through the 2 nd valve mechanism 62, but flows out of the outdoor heat exchanger 13 through the 1 st pipe 41.
During the heating operation, the liquid refrigerant flowing in through the 1 st pipe 41 flows into the 2 nd auxiliary heat exchanger 52, and is branched at the 1 st branch point P1 and flows into the 3 rd pipe 43. The liquid refrigerant flowing into the 2 nd auxiliary heat exchange portion 52 exchanges heat with outdoor air and is introduced into the auxiliary area 53B of the header 53. On the other hand, the liquid refrigerant flowing into the 3 rd pipe 43 is branched at the 2 nd branch point P2, flows through the 4 th pipe 44 to the 1 st auxiliary heat exchanger 51, and flows through the 5 th pipe 45 to the distributor 54. The liquid refrigerant flowing into the 1 st auxiliary heat exchange unit 51 exchanges heat with outdoor air and is introduced into the auxiliary area 53B of the header 53. On the other hand, the refrigerant flowing into the distributor 54 is distributed to a plurality of routes by the distributor 54 and introduced into the main heat exchange unit 50. The refrigerant introduced into the main heat exchange unit 50 exchanges heat with outdoor air in the main heat exchange unit 50, and is introduced into the main region 53A of the header 53. The 1 st valve mechanism 61 provided between the main area 53A and the auxiliary area 53B allows the flow of the refrigerant only in the direction from the auxiliary area 53B toward the main area 53A. Therefore, the refrigerant introduced into the auxiliary area 53B flows into the main area 53A, and merges with the refrigerant flowing from the main heat exchange unit 50 in the main area 53A. The refrigerant merged in the main region 53A flows out of the outdoor heat exchanger 13 through the 2 nd pipe 42.
As described above, according to embodiment 2, the 1 st valve mechanism 61 and the 2 nd valve mechanism 62 that allow the flow of the refrigerant only in one direction are provided on the route of the refrigerant in the outdoor heat exchanger 100, and the 2 nd auxiliary heat exchange unit 52 is provided in the 1 st pipe 41. Therefore, the route configuration corresponding to the flow of the refrigerant during the cooling operation and the flow of the refrigerant during the heating operation is formed, and the same effects as those of embodiment 1 can be obtained.
Further, according to embodiment 2, one of the valve mechanisms that permits the flow of the refrigerant only in one direction is replaced with the auxiliary heat exchange portion. Therefore, the number of valve mechanisms of the outdoor heat exchanger 100 can be reduced.
Embodiment 3
Fig. 5 is a view schematically showing the structure of an outdoor heat exchanger according to embodiment 3 of the present invention. In fig. 5, the same reference numerals are given to the same structural components as those in fig. 2 and 3. In fig. 5, solid arrows indicate the flow of the refrigerant during the cooling operation, and broken arrows indicate the flow of the refrigerant during the heating operation. The outdoor heat exchanger 101 according to embodiment 3 is provided with a three-way valve 110 in place of the 1 st valve mechanism 61, the 2 nd valve mechanism 62, and the 3 rd valve mechanism 63 described above in embodiment 1. The other structure is the same as embodiment 1. The three-way valve 110 has a 1 st port 111, a 2 nd port 112, a 3 rd port 113, and a movable mechanism portion 114. The 1 st port 111 is connected to the header 53 via the 8 th pipe 48. The 2 nd port 112 is connected to the 1 st pipe 41. The 3 rd port 113 is connected to the 3 rd pipe 43 extending to the side where the distributor 54 and the 1 st auxiliary heat exchanger 51 are located. One side of the movable mechanism 114 is connected to the 1 st pipe 41 via a pipe 121, and the other side is connected to the 2 nd pipe 42 via a pipe 122. Inside the movable mechanism portion 114, a movable member, not shown, is provided, which is displaced in accordance with the difference between the pressure of the refrigerant flowing through the 1 st pipe 41 and the pressure of the refrigerant flowing through the 2 nd pipe 42. The three-way valve 110 is configured to switch the opening and closing of the 1 st port 111, the 2 nd port 112, and the 3 rd port 113 according to the position of the movable member. The piping 121 and the piping 122 are connected to the movable mechanism portion 114 of the three-way valve 110 in order to obtain a pressure difference between the refrigerants, and do not constitute the piping of the refrigerant circuit 30 in fig. 1. Therefore, in fig. 5, the pipe 121 and the pipe 122 are indicated by dashed lines in order to be distinguished from other pipes constituting the refrigerant circuit 30.
When the pressure of the refrigerant flowing through the 2 nd pipe 42 is higher than the pressure of the refrigerant flowing through the 1 st pipe 41, the movable member of the movable mechanism portion 114 is displaced so that the 1 st port 111 and the 2 nd port 112 are opened, the 3 rd port 113 is closed, and the 1 st port 111 and the 2 nd port 112 are communicated with each other. When the pressure of the refrigerant flowing through the 1 st pipe 41 is higher than the pressure of the refrigerant flowing through the 2 nd pipe 42, the movable member of the movable mechanism portion 114 is displaced so that the 2 nd port 112 and the 3 rd port 113 are opened, the 1 st port 111 is closed, and the 2 nd port 112 and the 3 rd port 113 are communicated with each other. That is, the three-way valve 110 is an autonomous three-way valve that switches a path to be communicated with according to a pressure difference between the refrigerant flowing into the outdoor heat exchanger 101 and the refrigerant flowing out of the outdoor heat exchanger 101.
During the cooling operation, the refrigerant flows in from the 2 nd pipe 42, exchanges heat with the outside air in the main heat exchange portion 50 and the 1 st auxiliary heat exchange portion 51, and then flows out from the 1 st pipe 41. Since a pressure loss occurs in the heat exchange between the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51, the pressure of the refrigerant flowing through the 2 nd pipe 42 is higher than the pressure of the refrigerant flowing through the 1 st pipe 41 during the cooling operation. Therefore, the movable member of the movable mechanism 114 is displaced so that the 1 st port 111 and the 2 nd port 112 are opened, the 3 rd port 113 is closed, and the 1 st port 111 and the 2 nd port 112 are communicated with each other. As a result, the refrigerant flowing out of the distributor 54 flows only to the 1 st auxiliary heat exchange portion 51. The refrigerant flowing out of the header 53 flows through the 8 th pipe 48 and is introduced into the 1 st pipe 41 by the three-way valve 110. With this configuration, during the cooling operation, a route structure is formed in which the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51 are connected in series.
During the heating operation, the refrigerant flows in from the 1 st pipe 41, exchanges heat with the outside air in the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51, and then flows out from the 2 nd pipe 42. Since a pressure loss occurs in the heat exchange between the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51, the pressure of the refrigerant flowing through the 1 st pipe 41 is higher than the pressure of the refrigerant flowing through the 2 nd pipe 42 during the heating operation. Therefore, the movable member of the movable mechanism 114 is displaced so that the 2 nd port 112 and the 3 rd port 113 are opened, the 1 st port 111 is closed, and the 2 nd port 112 and the 3 rd port 113 are communicated with each other. As a result, the refrigerant flowing from the 1 st pipe 41 flows only to the 3 rd pipe 43 without flowing to the 8 th pipe 48 connected to the header 53 when passing through the three-way valve 110. With this configuration, during the heating operation, a route structure is formed in which the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51 are connected in parallel.
As described above, according to embodiment 3, the three-way valve 110, which autonomously changes the path according to the pressure difference between the refrigerant flowing into the outdoor heat exchanger 101 and the refrigerant flowing out of the outdoor heat exchanger 101, is provided on the route of the refrigerant in the outdoor heat exchanger 101. Therefore, the route structure suitable for both the cooling operation and the heating operation is configured without being controlled by the control device. As a result, the same effects as those of embodiments 1 and 2 described above can be obtained.
In embodiment 3, a plurality of 1 st auxiliary heat exchange units 51 may be provided, as in the modification of embodiment 1.
Embodiment 4
Fig. 6 is a diagram schematically showing the configuration around the outdoor heat exchanger in the outdoor unit of the refrigeration cycle apparatus according to embodiment 4 of the present invention. In fig. 6, the same components as those in fig. 1, 2, and 5 are denoted by the same reference numerals. In fig. 6, solid arrows indicate the flow of the refrigerant during the cooling operation, and broken arrows indicate the flow of the refrigerant during the heating operation. In the outdoor heat exchanger 102 according to embodiment 4, one side of the movable mechanism portion 114 of the three-way valve 110 is connected to the 2 nd pipe 42 via a pipe 123, and the other side is connected to the gas refrigerant pipe 31 via a pipe 124. The 2 nd pipe 42 is connected to a valve port communicating with the discharge side of the compressor 11 during the cooling operation and communicating with the suction side of the compressor 11 during the heating operation at the flow path switching portion 12. The gas refrigerant pipe 31 is connected to a valve port communicating with the suction side of the compressor 11 during the cooling operation and communicating with the discharge side of the compressor 11 during the heating operation at the flow path switching portion 12. The piping 123 and the piping 124 are connected to the movable mechanism portion 114 of the three-way valve 110 in order to obtain a pressure difference of the refrigerant, and do not constitute the piping of the refrigerant circuit 30 in fig. 1. Therefore, in fig. 6, the pipe 123 and the pipe 124 are indicated by dashed lines in order to be distinguished from other pipes constituting the refrigerant circuit 30.
When the pressure of the refrigerant flowing through the 2 nd pipe 42 is higher than the pressure of the refrigerant flowing through the gas refrigerant pipe 31, the movable member of the movable mechanism portion 114 is displaced so that the 1 st port 111 and the 2 nd port 112 are opened, the 3 rd port 113 is closed, and the 1 st port 111 and the 2 nd port 112 are communicated with each other. When the pressure of the refrigerant flowing through the gas refrigerant pipe 31 is higher than the pressure of the refrigerant flowing through the 2 nd pipe 42, the movable member of the movable mechanism portion 114 is displaced so that the 2 nd port 112 and the 3 rd port 113 are opened, the 1 st port 111 is closed, and the 2 nd port 112 and the 3 rd port 113 are communicated with each other. As described above, in embodiment 4, the three-way valve 110 is configured to switch the communication path according to the pressure difference between the refrigerant on the suction side of the compressor 11 and the refrigerant on the discharge side of the compressor 11. The other structure is the same as that of the outdoor heat exchanger 101 of embodiment 3.
During the cooling operation, the high-temperature high-pressure gas refrigerant compressed in the compressor 11 flows into the 2 nd pipe 42. On the other hand, a low-pressure gas refrigerant that flows out of the outdoor heat exchanger 13 and is sucked into the compressor 11 through the 1 st expansion valve 14, the 2 nd expansion valve 15, and the indoor heat exchanger 21 shown in fig. 1 flows into the gas refrigerant pipe 31. That is, during the cooling operation, the pressure of the refrigerant flowing through the 2 nd pipe 42 is higher than the pressure of the refrigerant flowing through the gas refrigerant pipe 31. Therefore, the movable member of the movable mechanism 114 is displaced so that the 1 st port 111 and the 2 nd port 112 are opened, the 3 rd port 113 is closed, and the 1 st port 111 and the 2 nd port 112 are communicated with each other. As a result, the refrigerant flowing out of the distributor 54 flows only to the 1 st auxiliary heat exchanger 51 at the 2 nd branch point P2. The refrigerant flowing out of the header 53 flows through the 8 th pipe 48 and is introduced into the 1 st pipe 41 through the three-way valve 110. With this configuration, a route structure is formed to connect the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51 in series during the cooling operation.
During the heating operation, the high-temperature and high-pressure gas refrigerant compressed by the compressor 11 flows into the gas refrigerant pipe 31. The gas refrigerant that has flowed into the gas refrigerant pipe 31 passes through the indoor heat exchanger 21, the 2 nd expansion valve 15, and the 1 st expansion valve 14 shown in fig. 1, and flows into the outdoor heat exchanger 102. On the other hand, the low-pressure gas refrigerant that has flowed out of the outdoor heat exchanger 102 and has been sucked into the compressor 11 flows into the 2 nd pipe 42. That is, during the heating operation, the pressure of the refrigerant flowing through the gas refrigerant pipe 31 is higher than the pressure of the refrigerant flowing through the 2 nd pipe 42. Therefore, the movable member of the movable mechanism 114 is displaced so that the 2 nd port 112 and the 3 rd port 113 are opened, the 1 st port 111 is closed, and the 2 nd port 112 and the 3 rd port 113 are communicated with each other. As a result, the refrigerant flowing in from the 1 st pipe 41 passes through the three-way valve 110, and flows only to the 3 rd pipe 43 without flowing into the 8 th pipe 48 connected to the header 53. With this configuration, during the heating operation, the route structure is formed in which the main heat exchange unit 50 and the 1 st auxiliary heat exchange unit 51 are connected in parallel.
As described above, in embodiment 4, the three-way valve 110, which autonomously changes the path according to the pressure difference between the refrigerant flowing into the outdoor heat exchanger 101 and the refrigerant flowing out of the outdoor heat exchanger 101, is provided in the path of the refrigerant in the outdoor heat exchanger 102. Therefore, the route structure suitable for both the cooling operation and the heating operation is configured without being controlled by the control device. As a result, the same effects as those of embodiments 1, 2, and 3 described above can be obtained. In embodiment 4, the three-way valve 110 is configured to operate in accordance with the difference in pressure between the refrigerant on the discharge side and the refrigerant on the suction side of the compressor 11. The pressure difference between the refrigerant on the discharge side and the refrigerant on the suction side of the compressor 11 is significant. Therefore, according to embodiment 4, the switching of the route configuration for each of the cooling operation and the heating operation is performed more reliably.
In embodiment 4, a plurality of 1 st auxiliary heat exchange units 51 may be provided, as in the modification of embodiment 1.
In embodiments 1 to 4 described above, the configuration of the outdoor heat exchanger 13 provided in the outdoor unit 10 serving as the heat source side unit is described, but the present invention is not limited thereto. The indoor heat exchanger 21 provided in the indoor unit 20 serving as the load-side unit may be configured in the same manner as the outdoor heat exchanger 13 described above.
Description of the reference numerals
1 … refrigeration cycle device; 10 … outdoor unit; 11 … compressor; 12 … flow path switching part; 13 … outdoor heat exchanger; 14 … expansion valve 1; 15 …, expansion valve 2; 16 … a refrigerant container; 20 … indoor unit; 21 … indoor heat exchanger; 30 … refrigerant circuit; 31 … a gas refrigerant pipe; 32 … liquid refrigerant piping; 41 …, 1 st pipe; 42 …, 2 nd pipe; 43 …, No. 3 pipe; 44 …, 4 th pipe; 45 …, 5 th pipe; 46 …, 6 th pipe; 47 …, 7 th pipe; 48 …, 8 th pipe; 50 … main heat exchange section; 51 …, 1 st auxiliary heat exchange section; 52 … item 2 auxiliary heat exchange section; a 53 … header; 53a … primary region; 53B … auxiliary area; 54 … dispenser; 61 … valve mechanism 1; 62 … valve mechanism 2; 63 … valve mechanism No. 3; 100 … outdoor heat exchanger; 101 … outdoor heat exchanger; 102 … outdoor heat exchanger; 110 … three-way valve; 111 … port 1; 112 … port 2; 113 port 3 of 113 …; 114 … movable mechanism part; 121 … piping; 122 … piping; 123 … piping; 124 … piping; 150 … heat transfer tubes; 151 … heat transfer tubes; 152 … heat transfer tubes; a P1 … branch point 1; a P2 … branch point 2; p3 … branch point 3.
Claims (13)
1. A heat exchanger having a heat transfer pipe through which a working fluid flows and a header connected to the heat transfer pipe and performing heat exchange between the working fluid and a gas,
it is characterized in that the preparation method is characterized in that,
the heat exchanger is provided with:
a main heat exchange unit having a plurality of the heat transfer tubes, and in which a plurality of routes of the working fluid are formed;
at least one 1 st auxiliary heat exchange portion having a smaller number of the heat transfer pipes than the main heat exchange portion and formed with a smaller number of routes of the working fluid than the main heat exchange portion;
a distributor that distributes the working fluid introduced to the main heat exchange portion to the plurality of routes;
a 1 st valve mechanism that is provided in the header between a main region of the heat transfer pipe connected to the main heat exchange portion and an auxiliary region of the heat transfer pipe connected to the 1 st auxiliary heat exchange portion, and that allows a flow of the working fluid only in a direction from the auxiliary region toward the main region; and
and a 2 nd valve mechanism that is provided between a 1 st pipe through which the working fluid flows into and out of the heat exchanger and the main heat exchange unit and the 1 st auxiliary heat exchange unit, and allows the working fluid flowing from the 1 st pipe to flow only in a direction from the 1 st pipe toward a side where the distributor and the 1 st auxiliary heat exchange unit are arranged.
2. The heat exchanger of claim 1,
the 1 st pipe is connected to the header, and the 1 st pipe is provided with a 3 rd valve mechanism, and the 3 rd valve mechanism prevents the working fluid flowing in from the 1 st pipe from flowing into the header and allows only the working fluid flowing out from the header to flow out from the 1 st pipe.
3. The heat exchanger of claim 1,
a 2 nd auxiliary heat exchange unit is provided between the header and the 1 st pipe, and the 2 nd auxiliary heat exchange unit has a smaller number of the heat transfer tubes than the main heat exchange unit and is formed with a smaller number of routes for the working fluid than the main heat exchange unit.
4. The heat exchanger of claim 1,
the 2 nd valve mechanism is a three-way valve configured to switch a path of communication according to a pressure difference between the working fluid flowing into the heat exchanger and the working fluid flowing out of the heat exchanger.
5. The heat exchanger of claim 4,
the three-way valve has:
a 1 st valve port connected to the manifold;
a 2 nd port connected to the 1 st pipe;
a 3 rd valve port connected with the distributor and the 1 st auxiliary heat exchange portion; and
a movable mechanism unit that switches opening and closing of the 1 st port, the 2 nd port, and the 3 rd port in accordance with a pressure difference between the working fluid flowing into the heat exchanger and the working fluid flowing out of the heat exchanger.
6. The heat exchanger of claim 5,
the movable mechanism switches the opening and closing of the 1 st port, the 2 nd port, and the 3 rd port according to a pressure difference between the working fluid flowing through the 2 nd pipe and the working fluid flowing through the 1 st pipe, the 2 nd pipe being connected to the header, and the working fluid flowing into and out of the 2 nd pipe in a direction opposite to a direction of the working fluid flowing into and out of the 1 st pipe.
7. The heat exchanger of claim 6,
the movable mechanism portion communicates the 1 st port with the 2 nd port when the working fluid flows in from the 2 nd pipe and flows out from the 1 st pipe, and communicates the 2 nd port with the 3 rd port when the working fluid flows in from the 1 st pipe and flows out from the 2 nd pipe.
8. The heat exchanger of claim 1,
the 1 st valve mechanism is a check valve.
9. The heat exchanger of claim 1,
the 2 nd valve mechanism is a check valve.
10. The heat exchanger of claim 2,
the 3 rd valve mechanism is a check valve.
11. The heat exchanger of claim 1,
has a plurality of the 1 st auxiliary heat exchange units.
12. A refrigeration cycle apparatus, wherein,
the heat exchanger according to claim 1 is provided.
13. A refrigeration cycle apparatus, comprising: an outdoor unit having a compressor and the heat exchanger of claim 4 or 5; and an indoor unit having an indoor heat exchanger,
it is characterized in that the preparation method is characterized in that,
the three-way valve is configured to switch a path to be communicated with the compressor in accordance with a pressure difference between the working fluid on a suction side of the compressor and the working fluid on a discharge side of the compressor.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2018/020168 WO2019225005A1 (en) | 2018-05-25 | 2018-05-25 | Heat exchanger and refrigeration cycle device |
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| Publication Number | Publication Date |
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| CN210772853U true CN210772853U (en) | 2020-06-16 |
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| CN201890000435.8U Expired - Fee Related CN210772853U (en) | 2018-05-25 | 2018-05-25 | Heat exchanger and refrigeration cycle device |
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| JP (1) | JPWO2019225005A1 (en) |
| CN (1) | CN210772853U (en) |
| WO (1) | WO2019225005A1 (en) |
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| CN113932485A (en) * | 2021-09-19 | 2022-01-14 | 青岛海尔空调器有限总公司 | Heat exchanger and refrigeration cycle system |
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| IN148686B (en) * | 1976-09-07 | 1981-05-09 | Carrier Corp | |
| JP4201990B2 (en) * | 2001-02-05 | 2008-12-24 | 三菱電機株式会社 | Air conditioner |
| JP5625691B2 (en) * | 2010-09-30 | 2014-11-19 | ダイキン工業株式会社 | Refrigeration equipment |
| JP5927415B2 (en) * | 2011-04-25 | 2016-06-01 | パナソニックＩｐマネジメント株式会社 | Refrigeration cycle equipment |
| WO2018029817A1 (en) * | 2016-08-10 | 2018-02-15 | 三菱電機株式会社 | Refrigeration cycle device |
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2018
- 2018-05-25 CN CN201890000435.8U patent/CN210772853U/en not_active Expired - Fee Related
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| JPWO2019225005A1 (en) | 2021-03-25 |
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