CN111065868B - Heat exchanger unit and refrigeration cycle device - Google Patents
Heat exchanger unit and refrigeration cycle device Download PDFInfo
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- CN111065868B CN111065868B CN201780094028.8A CN201780094028A CN111065868B CN 111065868 B CN111065868 B CN 111065868B CN 201780094028 A CN201780094028 A CN 201780094028A CN 111065868 B CN111065868 B CN 111065868B
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- 238000005057 refrigeration Methods 0.000 title claims description 31
- 239000003507 refrigerant Substances 0.000 claims abstract description 181
- 230000017525 heat dissipation Effects 0.000 claims description 77
- 230000001737 promoting effect Effects 0.000 claims description 57
- 239000007788 liquid Substances 0.000 claims description 38
- 238000009423 ventilation Methods 0.000 claims description 14
- 239000000203 mixture Substances 0.000 claims description 4
- 238000007664 blowing Methods 0.000 claims 2
- 238000001816 cooling Methods 0.000 description 18
- 238000002347 injection Methods 0.000 description 18
- 239000007924 injection Substances 0.000 description 18
- 230000004048 modification Effects 0.000 description 12
- 238000012986 modification Methods 0.000 description 12
- 238000005192 partition Methods 0.000 description 12
- 238000010586 diagram Methods 0.000 description 7
- 230000005855 radiation Effects 0.000 description 6
- 238000009826 distribution Methods 0.000 description 4
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 3
- 229910052782 aluminium Inorganic materials 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000006866 deterioration Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 230000020169 heat generation Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 230000005856 abnormality Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 238000005549 size reduction Methods 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
- 239000000758 substrate Substances 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Images
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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/20—Electric components for separate outdoor units
- F24F1/24—Cooling of electric components
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- 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
-
- 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/20—Electric components for separate outdoor units
- F24F1/22—Arrangement or mounting thereof
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
Abstract
The heat exchanger unit is provided with: a heat exchanger having a first heat exchange unit for exchanging heat with a refrigerant and a second heat exchange unit for exchanging heat with the refrigerant heat-exchanged by the first heat exchange unit; a blower that forms an air flow that passes air through the heat exchanger; and an electrical component box in which electrical components are stored, the electrical component box being provided closer to the second heat exchange unit than to the first heat exchange unit.
Description
Technical Field
The present invention relates to a heat exchanger unit including an electrical component box.
Background
A heat exchanger unit including an electrical component box has been known (see, for example, patent document 1). In patent document 1, the heat radiating fins attached to the electric component box are exposed in the heat exchange chamber, and the heat radiating fins are cooled by the air flowing into the heat exchange chamber.
Patent document 1: japanese patent laid-open publication No. 2016-166734
However, in patent document 1, the heat radiation of the electrical component box may be insufficient due to the positional relationship between the heat radiating fins and the heat exchange chamber. If the heat dissipation of the electrical component box is insufficient, there is a concern that electrical components housed in the electrical component box may deteriorate or be damaged.
Disclosure of Invention
The present invention has been made in view of the above-described problems, and an object thereof is to obtain a heat exchanger unit capable of efficiently dissipating heat from an electrical component box.
The heat exchanger unit according to the present invention includes: a heat exchanger having a first heat exchange unit for exchanging heat with a refrigerant and a second heat exchange unit for exchanging heat with the refrigerant heat-exchanged by the first heat exchange unit; a blower that forms an air flow that passes air through the heat exchanger; and an electrical component box in which electrical components are stored, the electrical component box being provided closer to the second heat exchange unit than to the first heat exchange unit.
According to the present invention, a heat exchanger unit capable of efficiently dissipating heat from an electrical component box can be obtained.
Drawings
Fig. 1 is a front view of a heat exchanger unit according to embodiment 1 of the present invention.
Fig. 2 is a view showing an example of the interior of the heat exchanger unit shown in fig. 1.
Fig. 3 is a view showing an example of the heat exchanger shown in fig. 2.
Fig. 4 is a diagram showing an example of a refrigeration cycle apparatus according to embodiment 1 of the present invention.
Fig. 5 is a view of the heat exchange chamber shown in fig. 2 as viewed from above.
Fig. 6 is a diagram showing an example of the configuration of the control device shown in fig. 1.
Fig. 7 is a diagram showing an example of the operation of the control device shown in fig. 6.
Fig. 8 is a view showing modification 1 of fig. 5.
Fig. 9 is a side view of the heat exchanger, the air path forming portion, and the heat dissipation promoting portion of fig. 8.
Fig. 10 is a view showing modification 2 of fig. 8.
Fig. 11 is a side view of the heat exchanger, the air path forming portion, and the heat dissipation promoting portion of fig. 10.
Fig. 12 is a diagram showing an example of a refrigeration cycle apparatus according to embodiment 2 of the present invention.
Description of reference numerals:
3 … heat exchanger; 3a … condenser; 10 … heat exchange chamber; 12 … a first fan shroud; 14 … a first blower; 16 … a second fan shroud; 18 … a second blower; 20 … machine room; 25 … a divider plate; 31 … a first heat exchanger; 31a … first heat exchange portion; 31B … second heat exchange portion; 32 … a second heat exchanger; 32a … third heat exchange portion; 32B … fourth heat exchange portion; 34 … second connecting pipe; 52 … compressor; 54 … a liquid storage portion; 54a … reservoir; 56 … subcooler; 58 … into an expansion valve; 100 … heat exchanger unit; 100a … heat exchanger unit; 101 … refrigeration cycle device; 101a … refrigeration cycle device; 102 … refrigerant circulation circuit; 103 … injection flow path; 110 … shell; 210 … electrical component box; 212 … heat dissipation facilitating portion; 213 … electrical components; 213a … temperature sensor; 214 … air path forming part; 214a … vent; 220 … control device; 310 … first flow into an outflow header; 310a … first inflow portion; 310B … first outflow portion; 310C … first partition; 311 … a first inflow pipe; 312 … first connection tube; 320C … second partition; 313 … a first outflow tube; 320 … second flow into the outflow header; 320a … second inflow; 320B … second outflow; 321 … a second inflow pipe; 322 … third connecting tube; 323 … a second outflow pipe; 400 … indoor unit; 402 … expansion valve; 404 … evaporator; 406 … fan; 410 … piping; 420 … piping.
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the drawings, the same or corresponding portions are denoted by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. In addition, the shape, size, arrangement, and the like of the structures shown in the drawings can be appropriately changed within the scope of the present invention.
Fig. 1 is a front view of a heat exchanger unit according to embodiment 1 of the present invention, fig. 2 is a view showing an example of the interior of the heat exchanger unit shown in fig. 1, fig. 3 is a view showing an example of the heat exchanger shown in fig. 2, fig. 4 is a view showing an example of a refrigeration cycle apparatus according to embodiment 1 of the present invention, and fig. 5 is a view showing a heat exchange chamber shown in fig. 2 as viewed from above. The heat exchanger unit 100 shown in fig. 1 is an outdoor unit installed outside a room. As shown in fig. 4, the present embodiment will be described mainly with respect to an example in which the heat exchanger 3 functions as the condenser 3A. The heat exchanger unit 100 is installed outdoors or in a machine room, for example, and is connected to the indoor unit 400 via a pipe 410 and a pipe 420. The pipe 410 is for flowing liquid refrigerant, and the pipe 420 is for flowing gas refrigerant. The indoor unit 400 is a cooling unit that is installed inside a room such as a warehouse and cools the inside of the room, for example. The indoor unit 400 may be a device that is installed in a showcase and cools the inside of the showcase. The indoor unit 400 has an expansion valve 402 and an evaporator 404. The expansion valve 402 expands the refrigerant. The evaporator 404 exchanges heat between the refrigerant and air to evaporate the refrigerant. A fan 406 is disposed in the vicinity of the evaporator 404. By operating the fan 406, air is taken in from the cooling space to the indoor unit 400, and the taken-in air passes through the evaporator 404, and the cold air heat-exchanged by the evaporator 404 is blown out to the cooling space.
[ Heat exchanger Unit ]
As shown in fig. 1 and 2, the heat exchanger unit 100 includes a casing 110 partitioned into a heat exchange chamber 10 and a machine chamber 20 by a partition plate 25. The heat exchanger 3 and the reservoir 54 are provided in the heat exchange chamber 10. The heat exchanger 3 exchanges heat between the refrigerant and air. Since the heat exchanger 3 is provided in the heat exchange chamber 10 partitioned by the partition plate 25 and the machine chamber 20, the heat exchanger 3 can efficiently perform heat exchange. The receiver 54 separates the gas-liquid two-phase refrigerant into a gas refrigerant and a liquid refrigerant, stores the liquid refrigerant, and discharges the gas refrigerant. The liquid reservoir 54 is provided at a lower portion of the inside of the heat exchange chamber 10. The liquid receiver 54 is provided at a low temperature position inside the heat exchange chamber 10, and thereby evaporation of the liquid refrigerant can be suppressed. The liquid reservoir 54 may be provided in the machine chamber 20.
As shown in fig. 1, a first blower 14 and a second blower 18 are provided in front of the heat exchange chamber 10. The first blower 14 and the second blower 18 form an air flow passing through the heat exchanger 3. The first blower 14 or the second blower 18 corresponds to a "blower" of the present invention. The first blower 14 is disposed closer to the first heat exchanger 31 than the second heat exchanger 32. The second blower 18 is provided below the first blower 14 and at a position closer to the second heat exchanger 32 than the first heat exchanger 31. A first fan shroud 12 is provided in front of the first blower 14, and a second fan shroud 16 is provided in front of the second blower 18. The heat exchanger unit 100 is provided with air intake portions, for example, on the left side portion and the rear side portion of the casing 110, and can intake air from the left side portion and the rear side portion. As shown in fig. 5, the first blower 14 or the second blower 18 operates to take in air from the back and the left side of the heat exchanger 3 and blow out air that has passed through the heat exchanger 3 from the front. That is, the heat exchanger unit 100 of the example of the present embodiment is a heat source unit of a side flow type that blows air in a direction intersecting the vertical direction. In the present embodiment, an example in which two blowers, i.e., the first blower 14 and the second blower 18, are provided is described, but the second blower 18 may be omitted and only the first blower 14 may be provided. Further, the air conditioner may be configured to include 3 or more air blowers including the first air blower 14, the second air blower 18, and other air blowers (not shown).
The machine room 20 is provided with a compressor 52, an electrical component box 210, refrigerant circuit components (not shown) such as connection pipes for controlling the flow of the refrigerant, and the like. The electrical component box 210 is attached to, for example, a partition plate 25 that partitions the heat exchange chamber 10 and the machine chamber 20. For example, the surface of electrical component box 210 on which heat dissipation promoting portion 212 is provided forms a part of partition plate 25. The electrical component box 210 is provided above the compressor 52. By providing the electrical component box 210 at the upper portion, convenience in maintenance and the like is improved. By providing the compressor 52 at the lower portion, the influence of the vibration of the compressor 52 can be reduced.
The electrical component box 210 houses electrical components 213, a temperature sensor 213a, a control device 220, and the like. The electrical component 213 generates a large amount of heat among the elements housed in the electrical component box 210. The electric component 213 includes, for example, an inverter that drives the compressor 52 or the first blower 14 or the second blower 18. The electrical component box 210 is provided with a heat dissipation promoting portion 212. The heat dissipation promoting portion 212 is for promoting heat dissipation of the electrical component 213, and is a heat sink made of a material having good thermal conductivity, such as aluminum. The heat dissipation promoting portion 212 is indirectly attached to the electrical component 213 via a substrate (not shown) on which the electrical component 213 is provided, for example. The heat dissipation promoting portion 212 may be directly attached to the electrical component 213. The heat dissipation promoting portion 212 enters the heat exchange chamber 10 and is exposed to the heat exchange chamber 10. The heat generated by the electrical components 213 and the like is discharged to the heat exchange chamber 10 via the heat dissipation promoting portion 212. The temperature sensor 213a directly or indirectly detects the temperature of the electrical component 213. The control device 220 performs overall control of the refrigeration cycle apparatus 101 shown in fig. 4, and is configured by, for example, a microcomputer or the like. The control device 220 may control the refrigeration cycle apparatus 101 together with a centralized controller (not shown) provided outside the heat exchanger unit 100 or a control device (not shown) provided in the indoor unit 400.
[ Heat exchanger ]
As shown in fig. 5, the heat exchanger 3 has a shape that is bent once, for example, and can efficiently perform heat exchange while saving space. The heat exchanger 3 may have a shape bent twice or more, or may not have a bent shape. As shown in fig. 2 and 3, the heat exchanger 3 includes a first heat exchanger 31 and a second heat exchanger 32. The first heat exchanger 31 and the second heat exchanger 32 are connected by a second connection pipe 34. The second connection pipe 34 is formed of a circular pipe having a flow path with a circular cross section. The refrigerant heat-exchanged by the first heat exchanger 31 passes through the second connection pipe 34 and is heat-exchanged by the second heat exchanger 32. The first heat exchanger 31 is provided above the second heat exchanger 32. The first heat exchanger 31 and the second heat exchanger 32 may be formed integrally.
The first heat exchanger 31 and the second heat exchanger 32 are formed to include: a refrigerant pipe having a flat shape and flowing a refrigerant therein; and a corrugated fin having a wave shape and connecting the refrigerant tubes to each other. The heat exchanger 3 of the example of the present embodiment is, for example, an aluminum flat tube corrugated fin heat exchanger in which flat tubes and corrugated fins are formed of aluminum, and weight reduction, cost reduction, size reduction, and the like are achieved. Since the refrigerant tube of the heat exchanger 3 has a flat shape, the heat exchange efficiency between the refrigerant and the air is improved, and the air passage resistance can be reduced. Further, since the refrigerant tube of the heat exchanger 3 has a flat shape, the heat exchanger 3 can be downsized and the amount of refrigerant to be charged can be reduced. Further, since the fins are corrugated fins having a wave shape, the heat transfer area can be increased.
The first heat exchanger 31 has a first heat exchange portion 31A and a second heat exchange portion 31B. The second heat exchange portion 31B is provided above the first heat exchange portion 31A. The first heat exchange unit 31A and the second heat exchange unit 31B have a plurality of flow paths through which the refrigerant flows in parallel. The first heat exchanger 31 has a first inflow/outflow header 310 attached to one end thereof, and a first connection pipe 312 attached to the other end thereof. The first inflow and outflow header 310 is formed of a circular tube having a flow path with a circular cross-section. The first inflow outflow header 310 has a first inflow portion 310A and a first outflow portion 310B. The first inflow portion 310A and the first outflow portion 310B are partitioned by a first partition portion 310C. The first inflow portion 310A is provided with a first inflow pipe 311, and the first outflow portion 310B is provided with a first outflow pipe 313. The first connecting pipe 312 is formed of a circular pipe having a flow path with a circular cross section. The first connection pipe 312 has a pipe diameter larger than 10mm in diameter. The refrigerant flowing in from the first inflow tube 311 is distributed to the first inflow portion 310A and flows in parallel in the first heat exchange portion 31A. The refrigerant flowing out of the first heat exchange unit 31A merges into the first connection pipe 312 and is distributed to flow in parallel in the second heat exchange unit 31B. The refrigerant flowing out of the second heat exchange portion 31B merges at the first outflow portion 310B and flows out of the first outflow pipe 313.
In the example of the present embodiment, as shown in fig. 1 and 2, since the electrical component box 210 is provided closer to the second heat exchange portion 31B than the first heat exchange portion 31A, the electrical component box 210 can efficiently dissipate heat. This is because the temperature of the second heat exchange portion 31B is lower than the temperature of the first heat exchange portion 31A. In the example of this embodiment, the electrical component box 210 is provided closer to the first outflow portion 310B serving as the refrigerant outflow portion of the second heat exchange portion 31B than the first connection pipe 312 serving as the refrigerant inflow portion of the second heat exchange portion 31B, so that the electrical component box 210 can efficiently dissipate heat. This is because the temperature of the refrigerant outflow portion of the second heat exchange portion 31B is lower than the temperature of the refrigerant inflow portion of the second heat exchange portion 31B.
As shown in fig. 2 and 3, the second heat exchanger 32 includes a third heat exchange portion 32A and a fourth heat exchange portion 32B. The third heat exchange portion 32A is provided above the fourth heat exchange portion 32B. The third heat exchange portion 32A and the fourth heat exchange portion 32B have a plurality of flow paths through which the refrigerant flows in parallel. In the second heat exchanger 32, a second inflow/outflow header 320 is attached to one end portion, and a third connection pipe 322 is attached to the other end portion. The second inflow and outflow header 320 is formed of a circular tube having a flow path with a circular cross section. The second inflow and outflow header 320 has a second inflow portion 320A and a second outflow portion 320B. The second inflow portion 320A and the second outflow portion 320B are partitioned by a second partition portion 320C. The second inflow portion 320A is provided with a second inflow pipe 321, and the second outflow portion 320B is provided with a second outflow pipe 323. The third connection pipe 322 is formed of a circular pipe having a flow path with a circular cross section. The refrigerant flowing in from the second inflow pipe 321 is distributed to the second inflow portion 320A and flows in parallel in the third heat exchange portion 32A. The refrigerant flowing out of the third heat exchange portion 32A merges into the third connection pipe 322, is distributed, and flows in parallel in the fourth heat exchange portion 32B. The refrigerant flowing out of the fourth heat exchange portion 32B merges at the second outflow portion 320B and flows out of the second outflow pipe 323.
[ flow of refrigerant in condenser ]
Next, the flow of the refrigerant in the condenser 3A will be described. The high-temperature and high-pressure gas refrigerant compressed by the compressor 52 shown in fig. 4 flows into the first heat exchange unit 31A through the first inflow pipe 311 and the first inflow portion 310A shown in fig. 3. The refrigerant that flows in the first heat exchange portion 31A in the direction intersecting the vertical direction and has exchanged heat with the air flows into the second heat exchange portion 31B above the first heat exchange portion 31A via the first connection pipe 312. The refrigerant that has exchanged heat with the air in the first heat exchange portion 31A becomes a gas refrigerant or a gas-liquid two-phase refrigerant having a high gas refrigerant ratio. In this embodiment, since the gas-liquid two-phase refrigerant having a high gas refrigerant or gas refrigerant ratio flows while rising through the first connection pipe 312, the influence of the pressure loss is reduced and the refrigerant distribution to the second heat exchange portion 31B is made uniform, as compared with the case where the gas-liquid two-phase refrigerant having a high liquid refrigerant or liquid refrigerant ratio flows while rising through the first connection pipe 312. This is because the density of the gaseous refrigerant is lower than that of the liquid refrigerant. Also, in this embodiment, since the first connection pipe 312 is formed of, for example, a circular pipe having a pipe diameter larger than 10mm, the influence of the pressure loss is reduced. Further, for example, by making the area of the first heat exchange portion 31A smaller than the area of the second heat exchange portion 31B, the ratio of the liquid refrigerant flowing to the first connection pipe 312 can be reduced, and therefore, the influence of the pressure loss can be further reduced, and the distribution of the refrigerant to the second heat exchange portion 31B can be further uniformized.
The refrigerant that has exchanged heat with the air while flowing in the direction intersecting the vertical direction in the second heat exchange unit 31B flows into the third heat exchange unit 32A below the first heat exchange unit 31A and the second heat exchange unit 31B via the first outflow portion 310B, the first outflow pipe 313, the second connection pipe 34, the second inflow pipe 321, and the second inflow portion 320A. The refrigerant that has exchanged heat with the air in the second heat exchange portion 31B becomes a gas-liquid two-phase refrigerant having a high ratio of the liquid refrigerant. In this embodiment, since the first heat exchange portion 31A is provided between the second heat exchange portion 31B and the third heat exchange portion 32A, the height difference between the second heat exchange portion 31B and the third heat exchange portion 32A can be increased. By increasing the height difference between the second heat exchange portion 31B and the third heat exchange portion 32A, the flow velocity of the refrigerant flowing into the second inflow portion 320A can be increased, and thus the distribution of the refrigerant flowing into the third heat exchange portion 32A can be made uniform. The gas-liquid two-phase refrigerant flowing into the third heat exchange portion 32A is made uniform, so that the heat exchange efficiency in the third heat exchange portion 32A is improved.
The refrigerant that has performed heat exchange with air while flowing in the direction intersecting the vertical direction in the third heat exchange portion 32A flows into the fourth heat exchange portion 32B via the third connection pipe 322. The refrigerant that has exchanged heat with the air in the third heat exchange portion 32A becomes a gas-liquid two-phase refrigerant in which the ratio of the liquid refrigerant is further increased. By configuring to flow the gas-liquid two-phase refrigerant having a high liquid refrigerant ratio downward, the influence of pressure loss can be reduced, and the refrigerant can be efficiently flowed. The refrigerant that has performed heat exchange with air while flowing in a direction intersecting the vertical direction in the fourth heat exchange portion 32B flows out of the second outflow pipe 323 via the second outflow portion 320B.
[ refrigeration cycle device ]
As shown in fig. 4, a refrigeration cycle apparatus 101 of the example of the embodiment includes: a refrigerant circulation circuit 102 for circulating a refrigerant; and an injection flow path 103 for returning the condensed refrigerant to the compressor 52. The refrigerant used in the refrigeration cycle device 101 of the embodiment is, for example, R410A, R32, or CO2The refrigerant having a low Global Warming Potential (GWP) may be a mixed refrigerant including at least one of them or another refrigerant different from them. Further, the refrigeration cycle apparatus 101 of the example of the embodiment can also use a zeotropic refrigerant mixture. The zeotropic refrigerant mixture is, for example, R407C or R448A. The zeotropic mixed refrigerant is R32, R125, R134a, R1234yf, CO2The mixed refrigerant of (1) may be a mixed refrigerant wherein the ratio XR32 (wt%) of R32 is 33 < XR32 < 39, the ratio XR125 (wt%) of R125 is 27 < XR125 < 33, the ratio XR134a (wt%) of R134a is 11 < XR134a < 17, the ratio XR1234yf (wt%) of R1234yf is 11 < XR1234yf < 17, CO2Ratio of (3) XCO2(wt%) 3 < XCO2Condition < 9, and XR32, XR125, XR134a, XR1234yf and XCO2The sum of (a) and (b) is 100.
The refrigerant circulation circuit 102 is a circuit in which the compressor 52, the condenser 3A, the reservoir 54, the subcooler 56, the expansion valve 402, and the evaporator 404 are connected by pipes. The compressor 52 compresses a refrigerant sucked therein, and discharges the refrigerant in a high-temperature and high-pressure state. The compressor 52 is, for example, an inverter compressor controlled by an inverter, and can change the capacity (the amount of refrigerant sent per unit time) by arbitrarily changing the operating frequency. The compressor 52 may be a constant speed compressor that operates at a constant operating frequency. In the example of the embodiment, an example in which 1 compressor 52 is provided is described, but the compressor 52 may have a plurality of compressors connected in parallel or in series. The condenser 3A condenses the refrigerant by exchanging heat between the refrigerant and air. The receiver 54 is a container for storing the refrigerant.
The subcooler 56 exchanges heat between the refrigerant flowing through the refrigerant circuit 102 and the refrigerant flowing through the injection flow path 103, and subcools the refrigerant flowing through the refrigerant circuit 102. The subcooler 56 is formed of, for example, a plate heat exchanger or a double-tube heat exchanger, and may be any device as long as it can exchange heat between the refrigerant flowing through the refrigerant circulation circuit 102 and the refrigerant flowing through the injection flow path 103. Although the subcooler 56 may be omitted, the degree of subcooling can be increased by providing the subcooler 56, and therefore the cooling capacity of the refrigeration cycle apparatus 101 can be increased.
The expansion valve 402 expands the refrigerant. The expansion valve 402 is formed of, for example, an electronic expansion valve or a temperature type expansion valve whose opening degree can be adjusted, but may be formed of a capillary tube whose opening degree cannot be adjusted. The expansion valve 402 may be formed by a combination of a plurality of flow paths connected in parallel by capillary tubes having different lengths and an on-off valve provided in at least one of the plurality of flow paths. The evaporator 404 evaporates the refrigerant. The evaporator 404 is, for example, a fin-and-tube heat exchanger including a pipe through which a refrigerant flows and a fin attached to the pipe.
The injection flow path 103 returns a part of the refrigerant condensed by the condenser 3A to the compressor 52. The injection flow path 103 is formed by a pipe connecting the subcooler 56 and the expansion valve 402 to a compression chamber (not shown) of the intermediate pressure of the compressor 52. The injection flow path 103 may be a pipe connecting the subcooler 56 and the expansion valve 402 to the low-pressure side of the compressor 52. The injection expansion valve 58 is provided in the injection flow path 103. The injection expansion valve 58 expands the refrigerant flowing into the injection flow path 103. The injection expansion valve 58 is formed of, for example, an electronic expansion valve or a temperature type expansion valve whose opening degree can be adjusted, but may be formed of a capillary tube whose opening degree cannot be adjusted. The injection expansion valve 58 may be formed by a combination of a plurality of flow paths connected in parallel by capillary tubes having different lengths and an on-off valve provided in at least one of the plurality of flow paths.
[ operation of refrigeration cycle apparatus ]
Next, the operation of the refrigeration cycle apparatus 101 will be described. The refrigerant compressed by the compressor 52 is condensed by the condenser 3A. The refrigerant condensed by the condenser 3A passes through the receiver 54 and is cooled by the subcooler 56. The refrigerant cooled by subcooler 56 is expanded by expansion valve 402. The refrigerant expanded by the expansion valve 402 is evaporated in the evaporator 404. The refrigerant evaporated by the evaporator 404 is sucked into the compressor 52 and compressed again. A part of the refrigerant cooled by the subcooler 56 is expanded by the injection expansion valve 58 of the injection flow path 103, passes through the subcooler 56 of the injection flow path 103, and returns to the compressor 52.
[ Cooling Structure of Electrical component Box ]
As shown in fig. 5, the heat dissipation promoting portion 212 exposed to the heat exchange chamber 10 is provided downstream of the heat exchanger 3 in the air flow. Specifically, the heat dissipation promoting portion 212 is provided at a position higher than the first partition portion 310C shown in fig. 3 and at a position where the air passing through the second heat exchange portion 31B passes. The air passing through the heat exchanger 3 is configured to pass through the heat dissipation promoting portion 212, thereby simplifying the cooling structure of the electrical component box 210. The heat exchanger unit 100 can be downsized by simplifying the cooling structure of the electrical component box 210. Since the air passing through the heat dissipation promoting portion 212 is the air passing through the second heat exchange portion 31B, the air passes through a lower temperature than the air passing through the first heat exchange portion 31A. Further, since the air passing through the heat dissipation promoting portion 212 becomes air passing through the vicinity of the first outflow portion 310B near the refrigerant outflow portion of the second heat exchange portion 31B, air having a lower temperature passes through than air passing through the vicinity of the first connection pipe 312 near the refrigerant inflow portion of the second heat exchange portion 31B. Since the temperature of the air passing through to the heat dissipation promoting portion 212 is set to a low temperature, the heat dissipation promoting portion 212 can efficiently dissipate heat. In a refrigeration apparatus or the like in which the heat exchanger 3 functions as the condenser 3A, the temperature of the refrigerant flowing into the heat exchanger 3 may be 100 degrees or higher. In this case, the heat exchanger 3 is configured such that the temperature of the refrigerant passing through the first outflow portion 310B is less than 60 degrees, so that the heat exchange efficiency of the heat exchanger 3 is improved and the heat radiation of the heat radiation promoting portion 212 can be efficiently performed.
[ operation of control device ]
Fig. 6 is a diagram showing an example of the configuration of the control device shown in fig. 1, and fig. 7 is a diagram showing an example of the operation of the control device shown in fig. 6. As shown in fig. 6, the control device 220 controls the first blower 14, the second blower 18, the compressor 52, the injection expansion valve 58, the expansion valve 402, the fan 406, and the like. When the indoor unit 400 shown in fig. 4 includes a control device (not shown), the control device 220 may control the first blower 14, the second blower 18, the compressor 52, or the injection expansion valve 58 of the heat exchanger unit 100, and the control device (not shown) of the indoor unit 400 may control the expansion valve 402 or the fan 406 of the indoor unit 400. For example, the controller 220 controls the first blower 14, the second blower 18, or the compressor 52 using the temperature of the electrical component 213 detected by the temperature sensor 213 a. As shown in fig. 7, in step S02, the refrigeration cycle device 101 shown in fig. 4 performs a normal operation.
In step S04 of fig. 7, it is determined whether or not the temperature of the electrical component 213 detected by the temperature sensor 213a is equal to or higher than a first threshold value. When the temperature of the electrical component 213 detected by the temperature sensor 213a is lower than the first threshold value, the process returns to step S02. When the temperature of the electrical component 213 detected by the temperature sensor 213a is equal to or higher than the first threshold value in step S04, the air volume of the first blower 14 shown in fig. 5 is increased and the air volume of the second blower 18 is maintained in step S06. Since the air volume passing through the heat dissipation promoting portion 212 is increased by increasing the air volume of the first blower 14, the heat dissipation of the electrical component 213 can be promoted. In this embodiment, when the temperature of the electrical component 213 is high, only the air volume of the first blower 14 and the second blower 18 needs to be increased, so that the power consumption can be reduced. When the temperature of the electrical component 213 is equal to or higher than the first threshold value, the rotation speed of the compressor 52 is not reduced or the compressor 52 is not stopped, so that the temperature rise in the cooling space is suppressed.
In step S08 of fig. 7, it is determined whether or not the temperature of the electrical component 213 detected by the temperature sensor 213a is equal to or higher than the second threshold value. The second threshold value is a value corresponding to a temperature higher than the first threshold value. When the temperature of the electrical component 213 detected by the temperature sensor 213a is lower than the second threshold value, the process returns to step S04. When the temperature of the electrical component 213 detected by the temperature sensor 213a is equal to or higher than the second threshold value in step S08, the rotation speed of the compressor 52 is reduced in step S10. The heat generation of the electric components 213 is suppressed by reducing the rotation speed of the compressor 52. In this embodiment, when the temperature of the electrical component 213 is equal to or higher than the second threshold value, the rotation speed of the compressor 52 is reduced without stopping the compressor 52, thereby suppressing the temperature increase of the cooling space.
In step S12, it is determined whether or not the temperature of the electrical component 213 detected by the temperature sensor 213a is equal to or higher than a third threshold value. The third threshold value is a value corresponding to a temperature higher than the second threshold value. When the temperature of the electrical component 213 detected by the temperature sensor 213a is lower than the third threshold value, the process returns to step S08. In step S12, if the temperature of the electrical component 213 detected by the temperature sensor 213a is equal to or higher than the third threshold value, the compressor 52 is stopped in step S14. The compressor 52 is stopped to suppress heat generation of the electrical components 213. In this embodiment, since the compressor 52 is stopped when the temperature of the electrical component 213 is equal to or higher than the third threshold value, deterioration or damage of the electrical component 213 can be suppressed. Further, by stopping the compressor 52 when the temperature of the electrical component 213 is equal to or higher than the third threshold value, it is possible to suppress a failure of the refrigeration cycle apparatus 101 or the like due to an abnormality of the first blower 14.
As described above, in the example of the present embodiment, since the cooling of the electrical component box 210 is promoted, the electrical component 213 can be prevented from becoming a high temperature equal to or higher than the first threshold value. Therefore, it is difficult to execute the protection control for eliminating the high temperature state of the electric component 213. In the example of the present embodiment, when the temperature of the electrical component 213 is equal to or higher than the first threshold value, the rotation speed of the compressor 52 is not reduced or the compressor 52 is not stopped, so that the temperature increase in the cooling space is suppressed. In the example of the present embodiment, when the temperature of the electrical component 213 is equal to or higher than the second threshold value, the rotation speed of the compressor 52 is reduced without stopping the compressor 52, thereby suppressing the temperature increase in the cooling space. Therefore, according to this embodiment, deterioration of the object to be cooled stored in the cooling space can be suppressed.
As described above, the heat exchanger unit 100 according to the example of the present embodiment includes: a heat exchanger 3 having a first heat exchange unit 31A for exchanging heat with a refrigerant and a second heat exchange unit 31B for exchanging heat with the refrigerant heat-exchanged by the first heat exchange unit 31A; a blower 14 that forms an air flow for passing air through the heat exchanger 3; and an electrical component box 210 in which an electrical component 213 is housed, the electrical component box 210 being provided closer to the second heat exchange unit 31B than to the first heat exchange unit 31A. The refrigeration cycle apparatus 101 according to the example of the present embodiment includes: a refrigerant circulation circuit 102 in which the compressor 52, the condenser 3A, the expansion valve 402, and the evaporator 404 are connected to circulate a refrigerant; and an electrical component box 210 in which an electrical component 213 is housed, the condenser 3A includes a heat exchanger 3, the heat exchanger 3 includes a first heat exchange portion 31A that exchanges heat with the refrigerant and a second heat exchange portion 31B that exchanges heat with the refrigerant that has been heat-exchanged by the first heat exchange portion 31A, and the electrical component box 210 is provided closer to the second heat exchange portion 31B than to the first heat exchange portion 31A. In the example of this embodiment, since the electrical component box 210 is provided close to the second heat exchange portion 31B having a lower temperature than the first heat exchange portion 31A, the electrical component box 210 can efficiently dissipate heat.
For example, the second heat exchange unit 31B includes a plurality of flow paths through which the refrigerant flows in parallel, and the electrical component box 210 can efficiently dissipate heat using air around the second heat exchange unit 31B having a lower temperature than the first heat exchange unit 31A.
Further, for example, since the electrical component box 210 is provided closer to the refrigerant outflow portion than the refrigerant inflow portion of the second heat exchange portion 31B, the electrical component box 210 can efficiently dissipate heat by air around the refrigerant outflow portion having a lower temperature than the refrigerant inflow portion of the second heat exchange portion 31B.
For example, the heat exchanger unit 100 includes a heat radiation promoting portion 212, and the heat radiation promoting portion 212 is provided at a position where the air passing through the second heat exchange portion 31B passes, and promotes heat radiation of the electrical component 213. By configuring to pass the air having passed through the second heat exchange portion 31B through the heat dissipation promoting portion 212, the cooling structure of the electrical component box 210 can be simplified. The heat exchanger unit 100 can be downsized by simplifying the cooling structure of the electrical component box 210.
For example, the case 110 has a heat exchange chamber 10 in which the heat exchanger 3 is housed and a machine chamber 20 in which the electrical component box 210 is housed, and the heat dissipation promoting portion 212 is exposed to the heat exchange chamber 10. Since the heat exchanger 3 is provided in the heat exchange chamber 10, the heat exchange of the heat exchanger 3 is more efficient, and the heat dissipation promoting portion 212 is exposed to the heat exchange chamber 10, the heat dissipation of the heat dissipation promoting portion 212 can be performed efficiently.
For example, the second heat exchange unit 31B is provided above the first heat exchange unit 31A, and the electrical component box 210 is provided at a position higher than the first heat exchange unit 31A. By providing the electrical component box 210 at a high position, convenience in maintenance and the like is improved.
For example, when the heat exchanger 3 functions as the condenser 3A and the second heat exchange unit 31B is provided above the first heat exchange unit 31A, the first connection pipe 312 connecting the first heat exchange unit 31A and the second heat exchange unit 31B is formed of a circular pipe, whereby the influence of pressure loss can be reduced. The first connection pipe 312 may be formed of, for example, a structure having a pipe diameter larger than 10mm in diameter.
For example, when the heat exchanger 3 functions as the condenser 3A and the second heat exchange unit 31B is provided above the first heat exchange unit 31A, the height difference between the second heat exchange unit 31B and the third heat exchange unit 32A can be increased by providing the third heat exchange unit 32A below the first heat exchange unit 31A. The third heat exchange portion 32A has a plurality of flow paths through which the refrigerant flows in parallel, and by increasing the height difference between the second heat exchange portion 31B and the third heat exchange portion 32A, the flow velocity of the refrigerant flowing through the second connection pipe 34 can be increased, and the distribution of the refrigerant flowing into the third heat exchange portion 32A can be made uniform. Further, the heat exchanger 3 is configured to include the first heat exchange portion 31A, the second heat exchange portion 31B, and the third heat exchange portion 32A, and thus the refrigerant passing through the first heat exchange portion 31A can be a gas refrigerant or a gas-liquid two-phase refrigerant having a high gas refrigerant ratio. The refrigerant flowing into the first connection pipe 312 connecting the first heat exchange portion 31A and the second heat exchange portion 31B becomes a gas refrigerant or a gas-liquid two-phase refrigerant having a high gas refrigerant ratio, whereby the influence of pressure loss can be reduced.
For example, the blower 14 includes a first blower 14 that blows air to the second heat exchange portion 31B and a second blower 18 that blows air to the third heat exchange portion 32A. By configuring the blower 14 to include the first blower 14 and the second blower 18, for example, the heat exchange amount in the second heat exchange portion 31B and the heat exchange amount in the third heat exchange portion 32A can be adjusted to efficiently exchange heat with the refrigerant.
For example, when the temperature detected by the temperature sensor 213a is equal to or higher than the first threshold, the air volume of the second blower 18 is maintained and the air volume of the first blower 14 is increased, thereby promoting the heat dissipation of the heat dissipation promoting portion 212. When the temperature of the electrical component 213 is high, only the air volume of the first blower 14 and the second blower 18 needs to be increased, so that the power consumption can be reduced. Then, when the temperature detected by the temperature sensor 213a becomes equal to or higher than a second threshold value corresponding to a temperature higher than the first threshold value, the rotation speed of the compressor 52 is reduced, and when the temperature detected by the temperature sensor 213a becomes equal to or higher than a third threshold value corresponding to a temperature higher than the second threshold value, the compressor 52 is stopped. In the example of the embodiment, even when the temperature of the electrical component 213 rises, the rotation speed of the compressor 52 is not immediately reduced or the compressor is not stopped, so that the temperature rise of the cooling space can be suppressed.
Further, for example, since the refrigerant tube of the heat exchanger 3 has a flat shape, the air passage resistance can be reduced, the heat exchange efficiency can be improved, and the heat exchanger 3 can be downsized.
Further, for example, the liquid reservoir 54 is provided at a low temperature position in the lower portion of the inside of the heat exchange chamber 10, and thereby evaporation of the liquid refrigerant can be suppressed.
In addition, in this embodiment, the above-described effect is significant when the heat exchanger 3 functions as the condenser 3A. This is because in a refrigeration apparatus or the like in which the heat exchanger 3 functions as the condenser 3A, the temperature of the refrigerant flowing into the heat exchanger 3 may be 100 degrees or higher. By providing the electrical component box 210 at a position where the influence of the high-temperature air having heat exchanged with the refrigerant of 100 degrees or more is small, the cooling structure of the electrical component box 210 can be simplified.
In addition, this embodiment provides a significant effect when the refrigerant is a non-azeotropic refrigerant mixture. This is because the temperature difference between the temperature of the refrigerant passing through the first heat exchange portion 31A and the temperature of the refrigerant passing through the second heat exchange portion 31B becomes large because the zeotropic refrigerant has a temperature gradient.
As described above, according to this embodiment, since the heat dissipation of the heat dissipation promoting portion 212 is more efficient, the heat dissipation promoting portion 212 can be downsized. By miniaturizing the heat dissipation promoting portion 212, the heat dissipation promoting portion 212 can be reduced in cost, the pressure loss in the air passage can be reduced, and the refrigeration cycle apparatus 101 can be miniaturized.
The present embodiment is not limited to the above description.
[ modification 1]
For example, fig. 8 is a view showing modification 1 of fig. 5, and fig. 9 is a side view of the heat exchanger, the air path forming portion, and the heat dissipation promoting portion of fig. 8. In fig. 8, the same components as those in fig. 5 are denoted by the same reference numerals, and the description thereof is omitted or simplified. As shown in fig. 8 and 9, modification 1 includes air path forming portion 214. The air path forming portion 214 forms an air path for allowing the air passing through the heat exchanger 3 to pass through the heat dissipation promoting portion 212. The air path forming portion 214 is provided downstream of the first heat exchanger 31A, and is attached to, for example, the partition plate 25 or the electrical component box 210. Air path forming portion 214 has a shape such that the flow speed of air passing through heat dissipation promoting portion 212 is higher than the flow speed of air passing through heat exchanger 3. For example, the air path forming portion 214 has a trumpet shape in which the opening area of the upstream air intake portion is formed larger than the downstream air intake portion. By forming the air intake portion of the air path forming portion 214 large, a large amount of air can be taken in and pass through the heat dissipation facilitating portion 212. The heat dissipation facilitating portion 212 is provided at a position higher than the first partition portion 310C of fig. 3. The air intake portion of the air path forming portion 214 is formed within the range of the second heat exchanger 31B, and can take in air that has passed through the second heat exchanger 31B. By passing the air having passed through the second heat exchange portion 31B through the heat dissipation promoting portion 212, the heat dissipation of the heat dissipation promoting portion 212 can be efficiently performed. For example, the opening of the air intake portion of the air path forming portion 214 may be formed to have a size 2 times or more the cross-sectional area of the heat dissipation promoting portion 212. In modification 1, since the air path forming portion 214 is provided, the amount of air passing through the heat dissipation facilitating portion 212 can be increased, and the speed of air passing through the heat dissipation facilitating portion 212 can be increased, thereby facilitating heat dissipation by the heat dissipation facilitating portion 212. In addition, in modification 1, since the air path forming portion 214 is provided, the heat dissipation facilitating portion 212 can be downsized.
[ modification 2]
Fig. 10 is a view showing modification 2 of fig. 8, for example, and fig. 11 is a side view of the heat exchanger, the air path forming portion, and the heat dissipation promoting portion of fig. 10. In fig. 10, the same components as those in fig. 8 are denoted by the same reference numerals, and the description thereof will be omitted or simplified. As shown in fig. 10 and 11, air path forming portion 214 of modification 2 includes ventilation portion 214A covering at least a portion of heat dissipation facilitating portion 212. The ventilation portion 214A is provided so as not to contact the heat dissipation facilitating portion 212, and can dissipate heat from the outer surface of the heat dissipation facilitating portion 212. A gap of, for example, 1 to 3mm is provided between the ventilation part 214A and the heat dissipation promoting part 212. By providing the ventilation portion 214A, air can be reliably blown to the heat dissipation promoting portion 212. Further, since the ventilation portion 214A is provided, the passage of high-temperature air that has passed through the first heat exchange portion 31A to the heat dissipation promoting portion 212 can be suppressed, and therefore, the heat dissipation of the heat dissipation promoting portion 212 is more efficient. The ventilation portion 214A may have a shape that covers at least a part of the heat dissipation facilitating portion 212, but the ventilation portion 214A may have a shape that covers the entire heat dissipation facilitating portion 212, thereby further securing the air flow to the heat dissipation facilitating portion 212. The ventilation portion 214A may be formed so that the velocity of air passing through the heat dissipation promoting portion 212 is 3m/sec or more. By forming the ventilation portion 214A so that the velocity of air passing through the heat dissipation promoting portion 212 is 3m/sec or more, the heat dissipation of the heat dissipation promoting portion 212 is made efficient. When the velocity of the air passing through the heat dissipation promoting portion 212 is less than 3m/sec due to the formation of the ventilation portion 214A, the ventilation portion 214A may be omitted as in modification 1. This is because, when the speed of the air passing through the heat dissipation promoting portion 212 is less than 3m/sec, high-temperature air having undergone heat exchange by the heat dissipation promoting portion 212 may be retained in the ventilation portion 214A. And because the ventilation part 214A is heated by the high-temperature air passing through the first heat exchange part 31A when the speed of the air passing through the heat dissipation promoting part 212 is less than 3m/sec, there is a fear that the heat dissipation of the heat dissipation promoting part 212 is blocked.
Embodiment 2.
Fig. 12 is a diagram showing an example of a refrigeration cycle apparatus according to embodiment 2 of the present invention. In fig. 12, the same components as those in fig. 4 are denoted by the same reference numerals, and the description thereof will be omitted or simplified. In embodiment 2, the same configuration as that of embodiment 1 will be omitted or simplified from description. As shown in fig. 12, the heat exchanger unit 100A of the refrigeration cycle apparatus 101A according to the example of the present embodiment is provided with the reservoir portion 54A between the first heat exchanger 31 and the second heat exchanger 32. The gas-liquid two-phase refrigerant flowing out of the first heat exchanger 31 is separated into a gas refrigerant and a liquid refrigerant in the receiver 54A, and the liquid refrigerant flows out of the receiver 54A. The liquid refrigerant flowing out of the receiver 54A is heat-exchanged in the second heat exchanger 32. In the example of this embodiment, the liquid refrigerant flowing out of the receiver 54A is heat-exchanged in the second heat exchanger 32, and therefore the degree of supercooling of the refrigerant flowing out of the heat exchanger 3 can be increased. Therefore, according to the example of this embodiment, the cooling capacity of the refrigeration cycle apparatus 101A can be increased.
The electrical component box 210 is disposed closer to the second heat exchanger 32 than the first heat exchanger 31. In embodiment 2, the first heat exchanger 31 corresponds to the "first heat exchange unit" of the present invention, and the second heat exchanger 32 corresponds to the "second heat exchange unit" of the present invention. Since the liquid refrigerant separated from the gas refrigerant in the receiver 54A flows through the second heat exchanger 32, the electrical component box 210 can efficiently dissipate heat by disposing the electrical component box 210 close to the second heat exchanger 32. This is because the temperature of the liquid refrigerant that has been separated from the gas refrigerant and has undergone heat exchange with the air is lower than the temperature of the gas-liquid two-phase refrigerant. The heat dissipation promoting portion 212 is provided at a position where the air passing through the second heat exchanger 32 passes, and the heat dissipation promoting portion 212 can efficiently dissipate the heat.
The present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the present invention. That is, the structure of the above embodiment may be suitably modified, and at least a part of the structure may be replaced with another structure. Further, the components not particularly limited in their arrangement are not limited to the arrangement disclosed in the embodiment, and may be arranged at positions where their functions are realized.
For example, embodiment 1 and embodiment 2 may be combined to provide a liquid reservoir between the first heat exchange portion 31A and the second heat exchange portion 31B of embodiment 1 shown in fig. 3. Further, a liquid reservoir may be provided between the first heat exchanger 31 and the second heat exchanger 32 in embodiment 1 shown in fig. 3, and the electrical component box 210 may be provided closer to the second heat exchanger 32 than the first heat exchanger 31.
For example, in embodiment 1 and embodiment 2, a description has been given of a refrigeration cycle apparatus applied to a large-sized refrigeration apparatus that cools the inside of a freezer or the like, but the refrigeration cycle apparatus can be applied to a small-sized refrigeration apparatus such as a refrigerator. The refrigeration cycle apparatus can also be applied to an air conditioner that cools or heats the inside of a room, and a heating apparatus that heats water or the like.
For example, in embodiment 1, the example in which the heat exchanger 3 functions as a condenser is described, but the heat exchanger 3 may function as an evaporator.
For example, in embodiment 1, the heat exchanger 3 including the first heat exchanger 31 and the second heat exchanger 32 provided below the first heat exchanger 31 is described, but embodiment 1 is not limited to this. For example, the heat exchanger 3 may be configured to include only the first heat exchanger 31 without the second heat exchanger 32, or may be configured to include 3 or more heat exchangers including the first heat exchanger 31, the second heat exchanger 32, and another heat exchanger.
For example, in embodiment 1, the present invention is directed to a display device including: the heat exchanger 3 including the first heat exchanger 31 having the first heat exchange portion 31A and the second heat exchange portion 31B, and the third heat exchange portion 32A and the fourth heat exchange portion 32B has been described, but the first heat exchange portion 31A, the second heat exchange portion 31B, the third heat exchange portion 32A, and the fourth heat exchange portion 32B may be formed independently of each other.
Claims (22)
1. A heat exchanger unit is characterized by comprising:
a heat exchanger having a first heat exchange unit for exchanging heat with a refrigerant and a second heat exchange unit for exchanging heat with the refrigerant heat-exchanged by the first heat exchange unit;
a blower that forms an air flow that passes air through the heat exchanger; and
an electrical component box for accommodating electrical components,
the heat exchanger is provided with:
an inflow unit that allows the refrigerant compressed by the compressor to flow into the first heat exchange unit having a plurality of flow paths that flow in parallel;
a connection pipe that allows the refrigerant flowing from the inflow portion to the first heat exchange portion to flow out to the second heat exchange portion having a plurality of flow paths that flow in parallel; and
an outflow portion that flows out the refrigerant heat-exchanged by the second heat exchange portion,
the electrical component box is provided closer to the second heat exchange portion than the first heat exchange portion and is provided closer to the outflow portion that becomes a refrigerant outflow portion of the second heat exchange portion than the connection pipe.
2. The heat exchanger unit of claim 1,
the heat exchanger unit includes a liquid reservoir provided between the first heat exchanger and the second heat exchanger.
3. The heat exchanger unit of claim 1,
the heat exchanger unit includes a heat dissipation promoting portion provided at a position where the air having passed through the second heat exchanging portion passes, and promoting heat dissipation of the electrical component.
4. Heat exchanger unit according to claim 3,
the heat exchanger unit includes a housing having a heat exchange chamber in which the heat exchanger is housed and a machine chamber in which the electrical component box is housed,
the heat dissipation promoting portion is exposed to the heat exchange chamber.
5. Heat exchanger unit according to claim 3,
the heat exchanger unit includes an air passage forming portion that forms an air passage for allowing the air that has passed through the heat exchanger to pass through the heat dissipation promoting portion,
the air path forming portion has a shape that allows air passing through the heat dissipation facilitating portion to flow faster than air passing through the heat exchanger.
6. The heat exchanger unit of claim 5,
the air passage forming portion includes an intake portion that takes in air to a range where the air passing through the second heat exchanger passes.
7. The heat exchanger unit of claim 5,
the air path forming portion has a ventilation portion that covers at least a part of the heat dissipation promoting portion.
8. Heat exchanger unit according to any of claims 1 to 7,
the second heat exchange portion is disposed at an upper portion of the first heat exchange portion.
9. The heat exchanger unit of claim 8,
the electric component box is disposed at a position higher than the first heat exchanging portion.
10. The heat exchanger unit of claim 8,
the heat exchanger includes a first connection pipe that is a pipe for allowing the refrigerant flowing out of the first heat exchange unit to flow into the second heat exchange unit and is formed of a circular pipe having a circular flow path.
11. The heat exchanger unit of claim 10,
the first connecting pipe has a pipe diameter of greater than 10mm in diameter.
12. Heat exchanger unit according to any of claims 1 to 7,
the heat exchanger includes a third heat exchange unit provided below the first heat exchange unit and configured to exchange heat with the refrigerant heat-exchanged by the second heat exchange unit.
13. The heat exchanger unit of claim 12,
the third heat exchange unit has a plurality of flow paths through which the refrigerant flows in parallel.
14. The heat exchanger unit of claim 12,
the air blower has a first air blower for blowing air to the second heat exchange portion and a second air blower for blowing air to the third heat exchange portion.
15. The heat exchanger unit of claim 14,
the heat exchanger unit is provided with a temperature sensor for detecting the temperature of the electrical component,
and if the temperature detected by the temperature sensor is more than a first threshold value, maintaining the air volume of the second blower and increasing the air volume of the first blower.
16. The heat exchanger unit of claim 15,
the heat exchanger unit is provided with the compressor for compressing refrigerant,
when the temperature detected by the temperature sensor is equal to or higher than a second threshold value corresponding to a temperature higher than the first threshold value, the rotation speed of the compressor is reduced,
and stopping the compressor when the temperature detected by the temperature sensor is equal to or higher than a third threshold value corresponding to a temperature higher than the second threshold value.
17. Heat exchanger unit according to any of claims 1 to 7,
the heat exchanger has a refrigerant tube formed in a flat shape.
18. The heat exchanger unit according to any one of claims 1 to 3 and 5 to 7,
the heat exchanger functions as a condenser.
19. The heat exchanger unit of claim 4,
the heat exchanger functions as a condenser.
20. The heat exchanger unit of claim 19,
the heat exchanger unit includes a receiver provided at a lower portion of the inside of the heat exchange chamber and configured to receive the refrigerant heat-exchanged by the heat exchanger.
21. The heat exchanger unit according to any one of claims 1 to 7, wherein the refrigerant is a non-azeotropic refrigerant mixture.
22. A refrigeration cycle device is characterized by comprising:
a refrigerant circulation circuit formed by connecting the compressor, the condenser, the expansion valve and the evaporator and used for circulating the refrigerant; and
an electrical component box for accommodating electrical components,
the condenser includes a heat exchanger having a first heat exchange portion for exchanging heat with a refrigerant and a second heat exchange portion for exchanging heat with the refrigerant after the heat exchange by the first heat exchange portion,
the heat exchanger is provided with:
an inflow unit that allows the refrigerant compressed by the compressor to flow into the first heat exchange unit having a plurality of flow paths that flow in parallel;
a connection pipe that allows the refrigerant flowing from the inflow portion to the first heat exchange portion to flow out to the second heat exchange portion having a plurality of flow paths that flow in parallel; and
an outflow portion that flows out the refrigerant heat-exchanged by the second heat exchange portion,
the electrical component box is provided closer to the second heat exchange portion than the first heat exchange portion and is provided closer to the outflow portion that becomes a refrigerant outflow portion of the second heat exchange portion than the connection pipe.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2017/030840 WO2019043771A1 (en) | 2017-08-29 | 2017-08-29 | Heat exchange unit and refrigeration cycle device |
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| Publication Number | Publication Date |
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| CN111065868A CN111065868A (en) | 2020-04-24 |
| CN111065868B true CN111065868B (en) | 2022-03-15 |
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| CN201780094028.8A Active CN111065868B (en) | 2017-08-29 | 2017-08-29 | Heat exchanger unit and refrigeration cycle device |
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| JP (1) | JP6888102B2 (en) |
| CN (1) | CN111065868B (en) |
| GB (1) | GB2579476B (en) |
| WO (1) | WO2019043771A1 (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP6935810B2 (en) * | 2019-07-18 | 2021-09-15 | ブラザー工業株式会社 | air conditioner |
| DE102021208945A1 (en) | 2021-08-16 | 2023-02-16 | Robert Bosch Gesellschaft mit beschränkter Haftung | Electronic device for a heat pump and heat pump device with such an electronic device |
| CN113883608B (en) * | 2021-10-14 | 2023-03-17 | 青岛海信日立空调系统有限公司 | Outdoor unit of multi-connected unit |
| WO2023132023A1 (en) * | 2022-01-06 | 2023-07-13 | 三菱電機株式会社 | Remote condenser unit, refrigeration cycle device, and refrigeration device |
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Also Published As
| Publication number | Publication date |
|---|---|
| GB202001225D0 (en) | 2020-03-11 |
| WO2019043771A1 (en) | 2019-03-07 |
| GB2579476A (en) | 2020-06-24 |
| JP6888102B2 (en) | 2021-06-16 |
| JPWO2019043771A1 (en) | 2020-04-23 |
| GB2579476B (en) | 2021-08-04 |
| CN111065868A (en) | 2020-04-24 |
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