WO2017094114A1 - 冷凍サイクル装置 - Google Patents
冷凍サイクル装置 Download PDFInfo
- Publication number
- WO2017094114A1 WO2017094114A1 PCT/JP2015/083751 JP2015083751W WO2017094114A1 WO 2017094114 A1 WO2017094114 A1 WO 2017094114A1 JP 2015083751 W JP2015083751 W JP 2015083751W WO 2017094114 A1 WO2017094114 A1 WO 2017094114A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat transfer
- flat heat
- transfer tube
- joint
- room
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
-
- 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
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0246—Arrangements for connecting header boxes with flow lines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F2009/0285—Other particular headers or end plates
- F28F2009/0287—Other particular headers or end plates having passages for different heat exchange media
Definitions
- the present invention relates to a refrigeration cycle apparatus using a hydrofluoroolefin refrigerant.
- a refrigerant having a lower global warming potential is also being studied for refrigerants used in refrigeration cycle apparatuses such as air conditioners.
- GWP global warming potential
- the G410 of R410A widely used for air conditioners is 2088, which is a very large value.
- the GWP of difluoromethane (R32), which has begun to be introduced in recent years, is also a considerably large value of 675.
- R744 Since the operating pressure is very high, there is a problem of ensuring a withstand pressure. Moreover, since critical temperature is as low as 31 degreeC, ensuring the performance in an air conditioner use becomes a subject. -R717: Since it is highly toxic, there is a problem of ensuring safety. -R290: Since it is highly flammable, there is a problem of ensuring safety.
- HFO refrigerants hydrofluoroolefin refrigerants having one double bond in the composition
- HFO refrigerants have low GWP values comparable to natural refrigerants, and by using these alone or in combination with an HFC refrigerant such as R32, a greenhouse gas reduction effect can be expected.
- the mixed refrigerant using HFO-1123 can be expected to have high performance. (For example, refer to Patent Document 1).
- the flat heat transfer tube has a flat shape such as a rectangular shape or an oval shape in cross section. And the several flow path through which a refrigerant
- the flat heat transfer tube has an advantage that heat transfer characteristics are improved because the heat transfer path is increased as compared with the circular heat transfer tube. Further, the flat heat transfer tube has an advantage that the air path resistance of the heat exchanger can be reduced because the cross-sectional shape thereof is flat. For this reason, a flat heat exchanger tube has a large performance improvement effect of an air conditioner compared with a circular heat exchanger tube.
- the material for forming the flat heat transfer tube As the material for forming the flat heat transfer tube, an aluminum alloy is often used from the viewpoint of workability. Further, it is difficult to bend the flat heat transfer tube because the internal flow path is crushed. For this reason, in a heat exchanger using a flat heat transfer tube, when bending the flow path in the heat exchanger, a configuration is adopted in which the ends of the flat heat transfer tubes are connected with a joint and the flow path is bent at the joint portion. Has been.
- HFO refrigerant has a low GWP, but has a short atmospheric life (HFO-1234yf: 11 days, HFO-1123: 1.6 days) and is easily decomposed. Further, when the HFO refrigerant is decomposed, a fluorine component comes out. This fluorine component reacts with nearby components, refrigeration oil additives, and the like, and is easily sludged.
- the decomposition reaction of the refrigerant generally occurs at the sliding portion of the compressor that tends to become high temperature, and the generated sludge circulates in the refrigeration cycle circuit together with the refrigerant and the refrigerator oil. Sludge generally has the property of dissolving in refrigerant and refrigeration oil at high temperatures and precipitating at sites where the temperature is low. In the refrigeration cycle circuit, the portion where the temperature changes from high temperature to low temperature is a portion from the vicinity of the center to the latter half (portion with subcool) in the flow path of the condenser.
- the flat heat transfer tube has a great effect of improving the heat transfer performance, but each flow passage becomes narrower. For this reason, when the heat exchanger using a flat heat exchanger tube is employ
- the present invention has been made to solve the above-described problems, and even if a heat exchanger using a flat heat transfer tube is employed in a refrigeration cycle circuit in which an HFO refrigerant is sealed, It aims at obtaining the refrigerating-cycle apparatus which can suppress that a flow path is blocked.
- a refrigeration cycle apparatus includes a refrigeration cycle circuit having a compressor, a condenser, and an expansion device, and a hydrofluoroolefin refrigerant encapsulated in the refrigeration cycle circuit.
- a first flow path composed of a first flat heat transfer tube having an end connected to the compressor, a second end having a plurality of flow paths inside, and a first end connected to the expansion device;
- a second flow path composed of a second flat heat transfer tube having a plurality of flow paths inside the second end, the first flat heat transfer tube, and the second flat heat transfer tube are connected, and the first flat heat transfer tube is connected.
- the joint has a recess inside the joint.
- the flow path of the condenser according to the present invention is a flow path in which a first flow path having a first flat heat transfer tube, a joint, and a second flow path having a second flat heat transfer tube are connected in series.
- the joint is located in the central portion of the condenser flow path or the latter half of the condenser flow path.
- the depositing sludge can be stored in the recessed part of a coupling. Therefore, the refrigeration cycle apparatus according to the present invention can suppress clogging of the flow paths of the first flat heat transfer tube and the second flat heat transfer tube due to the deposited sludge.
- FIG. 5 is a cross-sectional view taken along the line AA in FIG. 4.
- FIG. 8 is a sectional view taken along line AA in FIG.
- FIG. 8 is a sectional view taken along line BB in FIG.
- FIG. 11 is a sectional view taken along line BB in FIG. 10.
- FIG. 1 is a diagram showing a refrigeration cycle circuit 1 of a refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
- the refrigeration cycle circuit 1 includes a compressor 2, a condenser 10, an expansion device 5, and an evaporator 6, which are sequentially connected by a refrigerant pipe.
- the compressor 2 sucks refrigerant and compresses the refrigerant into a high-temperature and high-pressure gas refrigerant.
- the kind of the compressor 2 is not specifically limited,
- the compressor 2 can be comprised using various types of compression mechanisms, such as a reciprocating, a rotary, a scroll, or a screw.
- the compressor 2 may be configured of a type that can be variably controlled by an inverter.
- the condenser 10 exchanges heat between a refrigerant flowing inside and a heat exchange target such as air, and is, for example, a fin tube heat exchanger.
- the condenser 10 which concerns on this Embodiment 1 has the several flow path 11 arrange
- one end of these flow paths 11, that is, the end portion on the compressor 2 side is connected to the gas header 3, and the gas header 3 is connected to the discharge side of the compressor 2.
- the other ends of these flow paths 11 are connected to the liquid header 4, and the liquid header 4 is connected to the expansion device 5. That is, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 is branched to the respective flow paths 11 of the condenser 10 by the gas header 3.
- each flow path 11 joins the liquid header 4 and then flows into the expansion device 5.
- the expansion device 5 is an expansion valve, for example, and expands the refrigerant by decompressing it.
- the evaporator 6 exchanges heat between a refrigerant flowing inside and a heat exchange target such as air, and is, for example, a fin tube heat exchanger.
- the refrigeration cycle circuit 1 configured in this manner is filled with a hydrofluoroolefin refrigerant (HFO refrigerant) having one double bond in the composition.
- the HFO refrigerant may be sealed alone, a plurality of HFO refrigerants may be mixed and sealed, or a single or mixed HFO refrigerant.
- a mixed refrigerant of difluoromethane (R32) or the like may be enclosed. That is, the refrigeration cycle circuit 1 according to Embodiment 1 only needs to contain at least one of the HFO refrigerants.
- FIG. 2 is a perspective view showing the condenser 10, the gas header 3, and the liquid header 4 according to Embodiment 1 of the present invention.
- FIG. 3 is a cross-sectional view of the flat heat transfer tube 12 of the condenser 10 according to Embodiment 1 of the present invention cut along a cross section perpendicular to the flow path 13.
- FIG. 4 is a plan view of the joint 20 of the condenser 10 according to Embodiment 1 of the present invention.
- FIG. 5 is a cross-sectional view taken along the line AA in FIG.
- the flat heat transfer tube on the upstream side of the joint 20 may be referred to as a flat heat transfer tube 12a
- the flat heat transfer tube 12 on the downstream side of the joint 20 may be referred to as a flat heat transfer tube 12b. That is, the flat heat transfer tube 12 having the first end connected to the discharge side of the compressor 2 via the gas header 3 and the second end connected to the joint 20 may be referred to as a flat heat transfer tube 12a.
- the flat heat transfer tube 12 having the first end connected to the expansion device 5 via the liquid header 4 and the second end connected to the joint 20 may be referred to as a flat heat transfer tube 12b.
- the condenser 10 includes a plurality of flat heat transfer tubes 12, a plurality of fins 15, and a plurality of joints 20. As shown in FIG. 3, each of the flat heat transfer tubes 12 is partitioned by a partition wall, and a plurality of flow paths 13 communicating along the longitudinal direction of the flat heat transfer tubes 12 are formed.
- the flat heat transfer tubes 12a which are a part of the flat heat transfer tubes 12, are arranged in parallel in the vertical direction with a specified interval.
- the first end portions of these flat heat transfer tubes 12 a are connected to the gas header 3.
- a plurality of fins 15 that are juxtaposed along the longitudinal direction of the flat heat transfer tube 12a are attached to the flat heat transfer tubes 12a with a specified interval.
- the flat heat transfer tubes 12b which are the remaining part of the flat heat transfer tubes 12, are arranged in parallel in the vertical direction with a specified interval.
- the group of the flat heat transfer tubes 12b arranged side by side is juxtaposed in the lateral direction with respect to the group of the flat heat transfer tubes 12a arranged side by side.
- the first end of the flat heat transfer tube 12 b is connected to the liquid header 4.
- a plurality of fins 15 arranged in parallel along the longitudinal direction of the flat heat transfer tubes 12b are attached to the flat heat transfer tubes 12b with a specified interval.
- the flat heat transfer tubes 12 arranged as described above are arranged beside the flat heat transfer tubes 12a.
- the second end of the flat heat transfer tubes 12 a arranged side by side in the lateral direction and the second end of the flat heat transfer tubes 12 b are connected by a joint 20. That is, the flow path 11 of the condenser 10 is configured by connecting the flat heat transfer tube 12a, the joint 20, and the flat heat transfer tube 12b.
- the flow path 11 has a configuration in which the refrigerant flow is bent by 180 ° by the joint 20. And the flow path 11 comprised in this way becomes a structure arranged in parallel with a predetermined space
- the joint 20 is located in the center in the flow path 11 of the condenser 10.
- the flat heat transfer tube 12a corresponds to the first flat heat transfer tube and the first flow path of the present invention.
- the flat heat transfer tube 12b corresponds to the second flat heat transfer tube and the second flow path of the present invention.
- the joint 20 that connects the flat heat transfer tube 12a and the flat heat transfer tube 12b is a U-shaped pipe having a substantially U shape in plan view.
- a central portion of the joint 20 is a circular pipe portion 21 formed in a circular tube shape.
- both end portions of the joint 20 are flat-shaped portions 22 formed in a flat shape substantially the same shape as the cross section of the flat heat transfer tube 12.
- the joint 20 and the flat heat transfer tube 12 are connected by, for example, inserting an end portion of the flat heat transfer tube 12 into the flat shape portion 22 and performing brazing or the like.
- a deformed portion 23 is formed between the circular pipe portion 21 and the flat shape portion 22, whose cross-sectional shape is gradually deformed from a circular shape to a flat shape.
- a concave portion 24 that is recessed with respect to the surroundings is formed inside the circular pipe portion 21 of the joint 20.
- the recess 24 is formed on the entire circumference of the circular pipe portion 21.
- the gas refrigerant sucked into the compressor 2 is compressed by the compressor 2 and becomes a high-temperature gas refrigerant.
- the HFO refrigerant has a low GWP, but has a short atmospheric life (HFO-1234yf: 11 days, HFO-1123: 1.6 days) and is easily decomposed.
- the decomposition reaction of the HFO refrigerant generally occurs at a sliding portion of a compressor that tends to become high temperature.
- the fluorine component generated by the decomposition of the HFO refrigerant reacts with nearby components and the additive of the refrigerating machine oil and becomes sludge. This sludge dissolves in refrigerant and refrigerator oil at high temperatures. For this reason, the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the condenser 10 in a state where the sludge is dissolved.
- the high-temperature gas refrigerant discharged from the compressor 2 flows into the flow paths 11 of the condenser 10 through the gas header 3.
- the gas refrigerant flowing into each flow path 11 is cooled and condensed by a heat exchange target such as air supplied to the condenser 10.
- the gas refrigerant flowing into each flow path 11 of the condenser 10 exhibits the following temperature change.
- FIG. 6 is a diagram showing a temperature change of the refrigerant flowing through the flow path 11 of the condenser 10 according to Embodiment 1 of the present invention.
- shaft of FIG. 6 shows the edge part by the side of the gas header 3 in the flat heat exchanger tube 12a.
- the refrigerant outlet shown in FIG. 6 shows the edge part by the side of the liquid header 4 in the flat heat exchanger tube 12b.
- L / 2 shown in FIG. 6 indicates the intermediate position of the flow path 11, that is, the position of the joint 20.
- sludge dissolves in refrigerant and refrigeration oil at high temperatures. Then, as the refrigerant and the refrigerating machine oil are cooled, the sludge cannot be dissolved in these, and is deposited. That is, when the refrigerant is in a supercooled state in the flow path 11 of the condenser 10, sludge is likely to precipitate. As shown in FIG. 6, the refrigerant is supercooled in the flow path 11 slightly upstream (near the center) from the center of the flow path 11 when viewed in the flow direction of the refrigerant.
- sludge is likely to be generated slightly upstream from the center of the flow path 11, that is, slightly upstream to downstream of the joint 20. For this reason, there is a concern that the deposited sludge is clogged in each flow path 13 of the flat heat transfer tube 12 b located on the downstream side of the joint 20. Moreover, there is a concern that the refrigerant that has flowed out of the condenser 10 returns to the condenser 10 together with the sludge, and is clogged in each flow path 13 of the flat heat transfer tube 12a.
- the joint 20 is disposed at a position where sludge is likely to be deposited, and the concave portion 24 is formed in the joint 20.
- the sludge deposited on the upstream side of the joint 20 precipitates in the refrigerant, is stored in the lower part of the recess 24 of the joint 20, and circulates in the refrigeration cycle circuit 1. Removed from the refrigerant and refrigeration oil.
- the deposited sludge flows outward by centrifugal force when the refrigerant flowing in the joint 20 is bent, and is located on the outer side when the refrigerant is bent in the recess 24. It is stored in.
- sludge deposited on the downstream side of the joint 20 also circulates in the refrigeration cycle circuit 1 and is stored in the recess 24 of the joint 20 when returning to the flow path 11 of the condenser 10. Is removed from the refrigerant circulating in the refrigerant and the refrigeration oil. For this reason, the refrigeration cycle apparatus 100 according to the first embodiment can suppress clogging of each flow path 13 of the flat heat transfer tube 12 of the condenser 10 with sludge.
- the liquid refrigerant flowing out from each flow path 11 of the condenser 10 joins at the liquid header 4 and then flows into the expansion device 5 to expand.
- the temperature further decreases, and the refrigerant enters a gas-liquid two-phase state.
- the gas-liquid two-phase refrigerant flowing out of the expansion device 5 flows into the evaporator 6.
- the gas-liquid two-phase refrigerant flowing into the evaporator 6 is heated and evaporated by a heat exchange target such as air supplied to the evaporator 6. Then, the refrigerant that has flowed out of the evaporator 6 is sucked into the compressor 2 again.
- the precipitated sludge can be stored in the recess 24, it is possible to suppress clogging of each flow path 13 of the flat heat transfer tube 12 of the condenser 10 with sludge. it can.
- the concave portions 24 are formed at both ends of the circular pipe portion 21 of the joint 20.
- the concave portion 24 is formed at one end of the circular pipe portion 21, sludge can be stored in the concave portion 24, and each flow path 13 of the flat heat transfer tube 12 of the condenser 10 is clogged with sludge. This can be suppressed.
- the formation location of the recessed part 24 in the joint 20 is not limited to the circular pipe part 21, You may form the recessed part 24 in the flat shape part 22 or the deformation
- the recess 24 is arranged on the entire circumference of the joint 20 in the longitudinal section.
- the recess 24 is not necessarily provided on the entire circumference of the joint 20.
- a part of the inside of the joint 20 may be recessed to form the recess 24.
- most of the deposited sludge settles in the refrigerant and is stored in the lower part of the recess 24.
- FIG. 7 is a plan view showing another example of the joint 20 of the condenser 10 according to Embodiment 1 of the present invention.
- 8 is a cross-sectional view taken along the line AA in FIG.
- FIG. 9 is a sectional view taken along line BB in FIG.
- a recess 24 that is recessed downward with respect to the periphery is formed inside the flat portion 22. Even if the joint 20 is configured in this way, sludge can be stored in the recess 24, and each flow path 13 of the flat heat transfer tube 12 of the condenser 10 can be suppressed from being clogged with sludge.
- the joint 20 may be formed as follows.
- FIG. 10 is a plan view showing still another example of the joint 20 of the condenser 10 according to Embodiment 1 of the present invention.
- FIG. 11 is a cross-sectional view taken along the line AA in FIG.
- FIG. 12 is a cross-sectional view taken along the line BB in FIG.
- the joint 20 shown in FIGS. 10 to 12 includes, for example, a recess 24 that is recessed downward with respect to the periphery and a recess 24 that is recessed upward with respect to the periphery in the flat-shaped portion 22.
- the joint 20 By configuring the joint 20 in this way, when the joint 20 is mounted upside down and when the condenser 10 is installed upside down, the joint 20 always has a recess 24 that is recessed downward with respect to the surroundings. It will be. For this reason, sludge can be stored in the recess 24 even when the joint 20 is mounted upside down and when the condenser 10 is installed upside down.
- the two flat heat transfer tubes 12 connected by the joint 20 are arranged side by side in the horizontal direction, and the flow path 11 in which the flow of the refrigerant is bent in the horizontal direction is formed.
- two flat heat transfer tubes 12 connected by the joint 20 may be arranged in the vertical direction to form the flow path 11 in which the flow of the refrigerant is bent in the vertical direction.
- the joint 20 is configured as shown in FIG. 13, for example.
- FIG. 13 is a longitudinal sectional view of still another example of the joint 20 according to Embodiment 1 of the present invention as viewed from the front side.
- the joint 20 shown in FIG. 13 connects the flat heat transfer tubes 12 arranged side by side in the vertical direction.
- the recessed part 24 dented below rather than the periphery is formed in the inside of the flat shape part 22 used as the lower part of the coupling 20, for example.
- sludge can be stored in the recess 24, and each flow path 13 of the flat heat transfer tube 12 of the condenser 10 is clogged with sludge. This can be suppressed.
- either side of the flat heat transfer tubes 12 arranged side by side in the vertical direction may be the flat heat transfer tube 12a on the upstream side.
- the joint 20 may be formed as follows.
- FIG. 14 is a longitudinal sectional view of still another example of the joint 20 according to Embodiment 1 of the present invention as viewed from the front side.
- a concave portion 24 that is recessed below the periphery is formed in, for example, a flat-shaped portion 22 that is a lower portion.
- a concave portion 24 that is recessed upward from the periphery is formed in, for example, a flat-shaped portion 22 that is an upper portion.
- the concave portion 24 may be formed over the entire circumference of the joint 20.
- the flow path 11 of the condenser 10 has a configuration in which the flow of the refrigerant bends only once.
- the flow path 11 may be configured so that the flow of the refrigerant is not limited to this and is bent a plurality of times.
- FIG. 15 is a schematic diagram illustrating another example of the flow path 11 of the condenser 10 according to the first embodiment.
- FIG. 16 is an enlarged view of a main part when the condenser 10 employing the flow path 11 shown in FIG. 15 is viewed from the side.
- the white arrow shown in FIG.15 and FIG.16 has shown the flow direction of the refrigerant
- the two flow paths 11 are shown.
- the flow path 11 of the condenser 10 shown in FIGS. 15 and 16 is formed by connecting four flat heat transfer tubes 12 in series by three joints 20.
- the four flat heat transfer tubes 12 are arranged along the refrigerant flow direction, that is, from the gas header 3 to the liquid header 4 in the flat heat transfer tubes 12-1, 12-2, 12-3, 12-. It will be shown as 4. Further, the three joints 20 are shown along the refrigerant flow direction, that is, the joints 20-1, 20-2, 20-3 in the direction from the gas header 3 to the liquid header 4.
- the flat heat transfer tube 12-1, the joint 20-1, and the flat heat transfer tube 12-2 correspond to the first flow path of the present invention.
- the flat heat transfer tube 12-2 connected to the joint 20-2 corresponds to the first flat heat transfer tube of the present invention.
- the flat heat transfer tube 12-3, the joint 20-3, and the flat heat transfer tube 12-4 correspond to the second flow path of the present invention.
- the flat heat transfer tube 12-3 connected to the joint 20-2 corresponds to the second flat heat transfer tube of the present invention.
- the joint 20-3 arranged at a position 3/4 of the length of the flow path 11 in the flow direction of the refrigerant is configured as shown in FIG.
- the concave portion 24 may be formed in the joint 20-3. Sludge can be stored in the concave portion 24, and clogging of each flow path 13 of the flat heat transfer tube 12 of the condenser 10 with sludge can be suppressed.
- the flat heat transfer tube 12-1, the joint 20-1, the flat heat transfer tube 12-2, the joint 20-2, and the flat heat transfer tube 12-3 correspond to the first flow path of the present invention.
- the flat heat transfer tube 12-3 connected to the joint 20-3 corresponds to the first flat heat transfer tube of the present invention.
- the flat heat transfer tube 12-4 corresponds to the second flow path and the second flat heat transfer tube of the present invention. That is, the recess 24 may be formed in the joint 20 at a location where the length of the second flow path is equal to or less than the length of the first flow path.
- Embodiment 2 When each joint 20 is formed separately as in the first embodiment, depending on the number of joints 20, it takes time to braze each joint 20 and the flat heat transfer tube 12. May end up. In such a case, a plurality of joints 20 may be configured as one joint unit. In each of the following embodiments, a joint 20 that can be configured as a joint unit is introduced. Of course, the joint 20 introduced in each of the following embodiments may be manufactured individually instead of as a unit. In the following embodiments, items not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.
- FIG. 17 is a perspective view showing the condenser 10, the gas header 3, and the liquid header 4 according to Embodiment 2 of the present invention.
- the condenser 10 according to the second embodiment includes, for example, a rectangular parallelepiped joint unit 40 having a hollow inside.
- the interior of the joint unit 40 is divided into a plurality of spaces by a partition wall 41. That is, the joint unit 40 has a configuration in which a plurality of joints 20 having a room to which the flat heat transfer tube 12 is connected are connected in the vertical direction.
- each joint 20 has the following configuration.
- FIG. 18 is an enlarged view of a main part showing the joint 20 portion of the condenser 10 according to Embodiment 2 of the present invention.
- FIG. 18A is a cross-sectional view of the joint 20 viewed from the direction C in FIG. 17, that is, a plan cross-sectional view.
- FIG. 18B is a cross-sectional view of the joint 20 viewed from the direction D in FIG. 17, that is, a side vertical cross-sectional view.
- the joint 20 according to the second embodiment is formed in, for example, a rectangular parallelepiped having a hollow inside.
- the flat heat transfer tubes 12 a and 12 b constituting the same flow path 11 pass through the side surface 27 of the joint 20, in other words, are attached to the joint 20 so as to communicate with the internal space of the joint 20. That is, the internal space of the joint 20 and the peripheral wall thereof are a room 30 to which the flat heat transfer tubes 12a and 12b constituting the same flow path 11 are connected.
- the flat heat transfer tubes 12 a and 12 b configuring the same flow path 11 are arranged side by side in the horizontal direction and connected to the side surface 27.
- a portion below the flat heat transfer tubes 12a and 12b that is, a shaded portion in FIG.
- the refrigerant that has flowed into the room 30 of the joint 20 from the flat heat transfer tube 12a once stays in the room 30, and then flows into the flat heat transfer tube 12b. While the refrigerant stays in the chamber 30, the deposited sludge is stored in the recess 24.
- sludge can be stored in the recessed part 24 and it can suppress that each flow path 13 of the flat heat exchanger tube 12 of the condenser 10 is blocked with sludge.
- FIG. 19 is an essential part enlarged view showing a joint 20 portion of the condenser 10 according to Embodiment 3 of the present invention.
- FIG. 19A is a cross-sectional view of the joint 20 when the condenser 10 according to Embodiment 3 of the present invention is viewed from the direction C in FIG. 17, that is, a plan cross-sectional view.
- FIG. 19B is a sectional view of the joint 20 when the condenser 10 according to Embodiment 3 of the present invention is viewed from the direction D in FIG. 17, that is, a side longitudinal sectional view.
- the basic configuration of the joint 20 according to the third embodiment is the same as that of the joint 20 shown in the second embodiment.
- the difference between the joint 20 according to the third embodiment and the joint 20 shown in the second embodiment is the shape of the lower surface 26 of the room 30.
- the joint 20 according to the third embodiment is recessed below the range facing the flat heat transfer tube 12a on the lower surface 26 of the room 30 than in the range facing the flat heat transfer tube 12b on the lower surface 26 of the room 30. It has the 2nd recessed part 24a.
- the joint 20 is configured as in the third embodiment, sludge can be stored in the recess 24 and the second recess 24a, and each flow path 13 of the flat heat transfer tube 12 of the condenser 10 is clogged with sludge. Can be suppressed. Furthermore, the following effects can also be obtained by configuring the joint 20 as in the third embodiment. That is, the refrigerant flowing in the room 30 of the joint 20 flows out of the flat heat transfer tube 12a and flows into the flat heat transfer tube 12b. That is, the flow direction of the refrigerant in the room 30 is the horizontal direction.
- FIG. 20 is an essential part enlarged view showing a joint 20 portion of the condenser 10 according to Embodiment 4 of the present invention.
- 20A is a cross-sectional view of the joint 20 when the condenser 10 according to Embodiment 4 of the present invention is viewed from the direction C in FIG. 17, that is, a plan cross-sectional view.
- FIG. 20B is a sectional view of the joint 20 when the condenser 10 according to Embodiment 4 of the present invention is viewed from the direction D in FIG. 17, that is, a side longitudinal sectional view.
- the basic configuration of the joint 20 according to the fourth embodiment is the same as that of the joint 20 shown in the second embodiment.
- the joint 20 according to the fourth embodiment is different from the joint 20 shown in the second embodiment in that the room 30 is partitioned by a partition wall 29.
- the partition wall 29 partitions the room 30 of the joint 20 into a room 31 to which the flat heat transfer pipe 12a is connected and a room 32 to which the flat heat transfer pipe 12b is connected.
- the partition wall 29 is provided with a flow path 29 a penetrating the partition wall 29.
- the portion below the flow path 29a in the room 31 and the room 32 that is, the shaded portion in FIG.
- the room 31 corresponds to the first room of the present invention.
- the room 32 corresponds to the second room of the present invention.
- the flow path 29a corresponds to the third flow path of the present invention.
- the joint 20 is configured as in the fourth embodiment, sludge can be stored in the recess 24, and each flow path 13 of the flat heat transfer tube 12 of the condenser 10 can be prevented from being clogged with sludge. Furthermore, the following effects can also be obtained by configuring the joint 20 as in the fourth embodiment. That is, since the refrigerant flowing from the room 31 to the room 32 passes through the flow path 29a, the refrigerant is likely to stay in the recess 24 formed below the flow path 29a. For this reason, it can prevent that the sludge collected in the recessed part 24 is wound up, and can further suppress that each flow path 13 of the flat heat exchanger tube 12 of the condenser 10 is clogged with sludge.
- FIG. 21 is an enlarged view of a main part showing another example of the joint 20 according to Embodiment 4 of the present invention.
- the flow path 29a of the joint 20 shown in FIG. 21 is arrange
- FIG. 22 is an essential part enlarged view showing a joint 20 portion of the condenser 10 according to Embodiment 5 of the present invention.
- FIG. 22 is a sectional view of the joint 20 when the condenser 10 according to the fifth embodiment of the present invention is viewed from the direction C in FIG. 17, that is, a plan sectional view.
- the basic configuration of the joint 20 according to the fifth embodiment is the same as the joint 20 shown in any one of the second to fourth embodiments.
- the difference between the joint 20 according to the fifth embodiment and the joint 20 shown in any of the second to fourth embodiments is the position of the end of the flat heat transfer tube 12a in the joint 20.
- FIG. 22 shows the joint 20 according to the fifth embodiment, taking the joint 20 shown in the fourth embodiment as an example.
- the end of the flat heat transfer tube 12a protrudes into the chamber 30 of the joint 20.
- the distance L1 between the end of the flat heat transfer tube 12a connected to the room 30 and the side surface 28 of the room 30 facing the end is the side connected to the room 30 of the flat heat transfer tube 12b.
- the distance L2 is shorter than the distance L2 between this end and the side surface 28 of the room 30 facing the end.
- each flow path 13 of the flat heat transfer tube 12 of the condenser 10 is clogged with sludge. Further suppression is possible.
- the refrigeration cycle circuit 1 when using the joint 20 according to the fifth embodiment, it is preferable to enclose the refrigeration cycle circuit 1 with refrigeration oil to which an epoxy compound is added.
- Epoxy compounds are excellent in adhesiveness and are used as adhesive materials. For this reason, when the refrigerating machine oil to which the epoxy compound is added is sealed in the refrigeration cycle circuit 1, the sludge generated by reaction with the epoxy compound sticks to the side surface 28 when it collides with the side surface 28 of the room 30. Become. For this reason, since it can suppress that the sludge once captured in the room 30 flows out downstream, it can further suppress that each flow path 13 of the flat heat exchanger tube 12 of the condenser 10 is clogged with sludge.
- the position of the flow path 29a with respect to the flat heat transfer tube 12a is shown in FIG. It is preferable to set the position. That is, the flow path 29a is preferably closer to the side surface 27 to which the flat heat transfer tube 12a in the room 30 is connected than the end of the flat heat transfer tube 12a on the side protruding into the room 31.
- FIG. 23 is an essential part enlarged view showing a joint 20 portion of the condenser 10 according to Embodiment 6 of the present invention.
- FIG. 23A is a sectional view of the joint 20 when the condenser 10 according to Embodiment 6 of the present invention is viewed from the direction D in FIG. 17, that is, a side longitudinal sectional view.
- FIG. 23B is a cross-sectional view of the joint 20 when the condenser 10 according to Embodiment 6 of the present invention is viewed from the direction E of FIG. 17, that is, a rear vertical cross-sectional view.
- the flat heat transfer tubes 12 forming the same flow path 11 are arranged in the vertical direction, and the flow of the refrigerant in the joint 20 may be bent in the vertical direction.
- the joint 20 when the joint 20 is configured as one joint unit, the joint 20 may be configured as in the sixth embodiment.
- the joint 20 according to the sixth embodiment is formed in, for example, a rectangular parallelepiped having a hollow inside.
- the flat heat transfer tubes 12 a and 12 b constituting the same flow path 11 pass through the side surface 27 of the joint 20, in other words, are attached to the joint 20 so as to communicate with the internal space of the joint 20. That is, the internal space of the joint 20 and the peripheral wall thereof are a room 30 to which the flat heat transfer tubes 12a and 12b constituting the same flow path 11 are connected.
- the flat heat transfer tubes 12 a and 12 b constituting the same flow path 11 are arranged in the vertical direction and connected to the side surface 27.
- positioned above the flat heat exchanger tube 12b is shown. In the joint 20 configured as described above, the portion below the flat heat transfer tube 12b, that is, the shaded portion in FIG.
- FIG. 24 is an enlarged view of a main part showing another example of the joint 20 according to Embodiment 6 of the present invention.
- the distance L3 between the lower surface of the flat heat transfer tube 12b and the lower surface 26 of the room 30 is longer than the distance L4 between the upper surface of the flat heat transfer tube 12a and the upper surface 25 of the room 30. It has a configuration.
- the recess 24 can be formed larger, that is, more sludge can be stored in the recess 24, and each flow path 13 of the flat heat transfer tube 12 of the condenser 10 is clogged with sludge. This can be further suppressed.
- FIG. 25 is a principal part enlarged view showing a joint 20 portion of the condenser 10 according to Embodiment 7 of the present invention.
- 25A is a sectional view of the joint 20 when the condenser 10 according to Embodiment 7 of the present invention is viewed from the direction D in FIG. 17, that is, a side longitudinal sectional view.
- FIG. 25B is a sectional view of the joint 20 when the condenser 10 according to Embodiment 7 of the present invention is viewed from the direction E of FIG. 17, that is, a rear longitudinal sectional view.
- the basic configuration of the joint 20 according to the seventh embodiment is the same as that of the joint 20 shown in the sixth embodiment.
- the joint 20 according to the seventh embodiment is different from the joint 20 shown in the sixth embodiment in the position of the end portion of the flat heat transfer tube 12a in the joint 20.
- the end of the flat heat transfer tube 12a protrudes into the chamber 30 of the joint 20.
- the distance L1 between the end of the flat heat transfer tube 12a connected to the room 30 and the side surface 28 of the room 30 facing the end is the side connected to the room 30 of the flat heat transfer tube 12b.
- the distance L2 is shorter than the distance L2 between this end and the side surface 28 of the room 30 facing the end.
- each flow path 13 of the flat heat transfer tube 12 of the condenser 10 is clogged with sludge. Further suppression is possible.
- the refrigeration cycle circuit 1 When using the joint 20 according to the seventh embodiment, it is preferable to enclose the refrigeration cycle circuit 1 with refrigeration oil added with an epoxy compound.
- Epoxy compounds are excellent in adhesiveness and are used as adhesive materials. For this reason, when the refrigerating machine oil to which the epoxy compound is added is sealed in the refrigeration cycle circuit 1, the sludge generated by reaction with the epoxy compound sticks to the side surface 28 when it collides with the side surface 28 of the room 30. Become. For this reason, since it can suppress that the sludge once captured in the room 30 flows out downstream, it can further suppress that each flow path 13 of the flat heat exchanger tube 12 of the condenser 10 is clogged with sludge.
- 1 refrigeration cycle circuit 1 refrigeration cycle circuit, 2 compressor, 3 gas header, 4 liquid header, 5 expansion device, 6 evaporator, 10 condenser, 11 flow path, 12 (12a, 12b) flat heat transfer tube, 13 flow path, 15 fin, 20 Joint, 21 circular pipe part, 22 flat part, 23 deformed part, 24 recessed part, 24a second recessed part, 25 upper face, 26 lower face, 27 side face, 28 side face, 29 partition wall, 29a flow path, 30 room, 31 room, 32 rooms, 40 joint units, 41 partition walls, 100 refrigeration cycle equipment.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
・R717:高毒性であるため、安全確保の課題がある。
・R290:強燃性であるため、安全確保の課題がある。
図1は、本発明の実施の形態1に係る冷凍サイクル装置100の冷凍サイクル回路1を示す図である。
冷凍サイクル回路1は、圧縮機2、凝縮器10、膨張装置5及び蒸発器6を有しており、これらが順次冷媒配管で接続されて構成されている。
なお、凝縮器10の詳細構成については、後述する。
図2は、本発明の実施の形態1に係る凝縮器10、ガスヘッダ3及び液ヘッダ4を示す斜視図である。図3は、本発明の実施の形態1に係る凝縮器10の扁平伝熱管12を流路13と垂直な断面で切断した断面図である。図4は、本発明の実施の形態1に係る凝縮器10の継手20の平面図である。図5は、図4のA-A断面図である。
ここで、扁平伝熱管12aが、本発明の第1扁平伝熱管及び第1流路に相当する。扁平伝熱管12bが、本発明の第2扁平伝熱管及び第2流路に相当する。
続いて、このように形成された冷凍サイクル装置100の動作について説明する。
図7~図9に示す継手20は、例えば、扁平形状部22の内部に、周囲に対して下方に凹んだ凹部24が形成されている。このように継手20を構成しても、凹部24にスラッジを貯留することができ、凝縮器10の扁平伝熱管12の各流路13がスラッジで詰まることを抑制できる。
図10~図12に示す継手20は、例えば、扁平形状部22の内部に、周囲に対して下方に凹んだ凹部24と、周囲に対して上方に凹んだ凹部24とを備えている。このように継手20を構成することにより、継手20を上下逆に取り付けた際、及び、凝縮器10を上下逆に設置した際、継手20は必ず周囲に対して下方に凹んだ凹部24を有することとなる。このため、継手20を上下逆に取り付けた際、及び、凝縮器10を上下逆に設置した際でも、凹部24にスラッジを貯留することができる。
図13に示す継手20は、縦方向に並んで配置された扁平伝熱管12を接続している。そして、継手20の下側部分となる例えば扁平形状部22の内部には、周囲よりも下方に凹んだ凹部24が形成されている。このような継手20を用いて凝縮器10の各流路11を形成しても、凹部24にスラッジを貯留することができ、凝縮器10の扁平伝熱管12の各流路13がスラッジで詰まることを抑制できる。なお、縦方向に並んで配置された扁平伝熱管12は、どちら側が上流側の扁平伝熱管12aになってもよい。
図14に示す継手20は、下側部分となる例えば扁平形状部22の内部に、周囲よりも下方に凹んだ凹部24が形成されている。さらに、図14に示す継手20は、上側部分となる例えば扁平形状部22の内部に、周囲よりも上方に凹んだ凹部24が形成されている。このように継手20を構成することにより、継手20を上下逆に取り付けた際、及び、凝縮器10を上下逆に設置した際、継手20は必ず周囲に対して下方に凹んだ凹部24を有することとなる。このため、継手20を上下逆に取り付けた際、及び、凝縮器10を上下逆に設置した際でも、凹部24にスラッジを貯留することができる。
なお、縦方向に並んだ扁平伝熱管12を継手20で接続する際、図4及び図5で示したように、継手20の周囲全周にわたって凹部24を形成しても勿論よい。
図15及び図16に示す凝縮器10の流路11は、4つの扁平伝熱管12を3つの継手20によって直列に接続することにより形成されている。なお、説明の便宜上、4つの扁平伝熱管12を、冷媒の流れ方向に沿って、つまりガスヘッダ3から液ヘッダ4の方向に、扁平伝熱管12-1,12-2,12-3,12-4と示すこととする。また、3つの継手20を、冷媒の流れ方向に沿って、つまりガスヘッダ3から液ヘッダ4の方向に、継手20-1,20-2,20-3を示すこととする。
実施の形態1のように各継手20を別々に形成した場合、継手20の数によっては、各継手20と扁平伝熱管12のろう付けに時間がかかる等、凝縮器10の組立工数が増大してしまう場合がある。このような場合、複数の継手20を1つの継手ユニットとして構成してもよい。以下の各実施の形態において、継手ユニットとして構成できる継手20を紹介する。なお、以下の各実施の形態で紹介する継手20を、ユニットとしてではなく個別に製作しても勿論よい。また、以下の各実施の形態において、特に記述しない項目については実施の形態1と同様とし、同一の機能や構成については同一の符号を用いて述べることとする。
本実施の形態2に係る凝縮器10は、内部が空洞となった例えば直方体の継手ユニット40を備えている。この継手ユニット40の内部は、仕切壁41によって複数の空間に区切られている。つまり、継手ユニット40は、扁平伝熱管12の接続される部屋を有する継手20が上下方向に複数連なった構成となっている。本実施の形態2では、各継手20は、以下のような構成となっている。
扁平伝熱管12aから継手20の部屋30に流入した冷媒は、部屋30で一旦滞留した後、扁平伝熱管12bに流入する。この部屋30に冷媒が滞留している間に、析出したスラッジが凹部24に貯留される。
図19は、本発明の実施の形態3に係る凝縮器10の継手20部分を示す要部拡大図である。なお、図19(A)は、本発明の実施の形態3に係る凝縮器10を図17のC方向から見た際の継手20の断面図、つまり平面断面図となっている。また、図19(B)は、本発明の実施の形態3に係る凝縮器10を図17のD方向から見た際の継手20の断面図、つまり側面縦断面図となっている。
図20は、本発明の実施の形態4に係る凝縮器10の継手20部分を示す要部拡大図である。なお、図20(A)は、本発明の実施の形態4に係る凝縮器10を図17のC方向から見た際の継手20の断面図、つまり平面断面図となっている。また、図20(B)は、本発明の実施の形態4に係る凝縮器10を図17のD方向から見た際の継手20の断面図、つまり側面縦断面図となっている。
ここで、部屋31が、本発明の第1部屋に相当する。部屋32が、本発明の第2部屋に相当する。また、流路29aが、本発明の第3流路に相当する。
図21は、本発明の実施の形態4に係る継手20の別の一例を示す要部拡大図である。
図21に示す継手20の流路29aは、扁平伝熱管12aよりも高い位置に配置されている。このように継手20を構成することにより、流路29aと扁平伝熱管12aの高さが異なるため、扁平伝熱管12aから部屋31に流入した冷媒は、流路29aに直接流れ込むことができなくなる。このため、扁平伝熱管12aから部屋31に流入した冷媒は、一旦部屋31で滞留した後に部屋32に流入することとなり、スラッジが部屋32に流入しづらくなる。したがって、部屋32に貯留されているスラッジが扁平伝熱管12bに流れ込むことを抑制できるので、凝縮器10の扁平伝熱管12の各流路13がスラッジで詰まることをさらに抑制できる。
図22は、本発明の実施の形態5に係る凝縮器10の継手20部分を示す要部拡大図である。この図22は、本発明の実施の形態5に係る凝縮器10を図17のC方向から見た際の継手20の断面図、つまり平面断面図となっている。
図23は、本発明の実施の形態6に係る凝縮器10の継手20部分を示す要部拡大図である。なお、図23(A)は、本発明の実施の形態6に係る凝縮器10を図17のD方向から見た際の継手20の断面図、つまり側面縦断面図となっている。また、図23(B)は、本発明の実施の形態6に係る凝縮器10を図17のE方向から見た際の継手20の断面図、つまり背面縦断面図となっている。
このように構成された継手20においては、扁平伝熱管12bよりも下方の部分、つまり図23の網掛け部分が凹部24となる。
図24は、本発明の実施の形態6に係る継手20の別の一例を示す要部拡大図である。
図24に示す継手20においては、扁平伝熱管12bの下面と部屋30の下面26との間の距離L3は、扁平伝熱管12aの上面と部屋30の上面25との間の距離L4よりも長い構成となっている。このように構成することにより、凹部24をより大きく形成することができ、つまり凹部24により多くのスラッジを貯留することができ、凝縮器10の扁平伝熱管12の各流路13がスラッジで詰まることをより抑制できる。
図25は、本発明の実施の形態7に係る凝縮器10の継手20部分を示す要部拡大図である。なお、図25(A)は、本発明の実施の形態7に係る凝縮器10を図17のD方向から見た際の継手20の断面図、つまり側面縦断面図となっている。また、図25(B)は、本発明の実施の形態7に係る凝縮器10を図17のE方向から見た際の継手20の断面図、つまり背面縦断面図となっている。
Claims (13)
- 圧縮機、凝縮器及び膨張装置を有する冷凍サイクル回路と、
前記冷凍サイクル回路に封入された、ハイドロフルオロオレフィン系冷媒と、
を備え、
前記凝縮器は、
第1端部が前記圧縮機に接続され、第2端部が内部に複数の流路を有する第1扁平伝熱管で構成された第1流路と、
第1端部が前記膨張装置に接続され、第2端部が内部に複数の流路を有する第2扁平伝熱管で構成された第2流路と、
前記第1扁平伝熱管と前記第2扁平伝熱管とが接続され、前記第1扁平伝熱管と前記第2扁平伝熱管との間の前記ハイドロフルオロオレフィン系冷媒の流れを曲げる継手と、
を備え、
前記第2流路の長さは前記第1流路の長さ以下であり、
前記継手は、該継手の内部に凹部を有する冷凍サイクル装置。 - 前記第1扁平伝熱管及び前記第2扁平伝熱管は、横方向に並んで配置されており、
前記継手は、側面に前記第1扁平伝熱管及び前記第2扁平伝熱管が接続された部屋を有し、
前記部屋における前記第1扁平伝熱管及び前記第2扁平伝熱管よりも下方の部分が、前記凹部を構成する請求項1に記載の冷凍サイクル装置。 - 前記部屋の下面における前記第1扁平伝熱管と対向する範囲に、前記部屋の下面における前記第2扁平伝熱管と対向する範囲よりも下方に凹んだ第2凹部を有する請求項2に記載の冷凍サイクル装置。
- 前記第1扁平伝熱管及び前記第2扁平伝熱管は、横方向に並んで配置されており、
前記継手は、
側面に前記第1扁平伝熱管及び前記第2扁平伝熱管が接続された部屋と、
前記部屋を、前記第1扁平伝熱管が接続された第1部屋と前記第2扁平伝熱管が接続され第2部屋とに仕切る仕切壁と、
前記仕切壁を貫通する第3流路と、
を備え、
前記部屋における前記第3流路よりも下方の部分が、前記凹部を構成する請求項1に記載の冷凍サイクル装置。 - 前記第3流路は、前記第1扁平伝熱管よりも高い位置に配置されている請求項4に記載の冷凍サイクル装置。
- 前記第1扁平伝熱管の端部は、前記部屋の内部に突出しており、
前記第3流路は、前記第1扁平伝熱管における前記部屋に突出した側の端部よりも、前記部屋における前記第1扁平伝熱管が接続された側面に近い請求項4又は請求項5に記載の冷凍サイクル装置。 - 前記第1扁平伝熱管及び前記第2扁平伝熱管は、縦方向に並んで配置されており、
前記継手は、側面に前記第1扁平伝熱管及び前記第2扁平伝熱管が接続された部屋を有し、
前記部屋において、前記第1扁平伝熱管及び前記第2扁平伝熱管のうちで下側に配置された扁平伝熱管よりも下方の部分が、前記凹部を構成する請求項1に記載の冷凍サイクル装置。 - 前記第1扁平伝熱管及び前記第2扁平伝熱管のうちで下側に配置された扁平伝熱管の下面と前記部屋の下面との間の距離は、前記第1扁平伝熱管及び前記第2扁平伝熱管のうちで上側に配置された扁平伝熱管の上面と前記部屋の上面との間の距離よりも長い請求項7に記載の冷凍サイクル装置。
- 前記第1扁平伝熱管における前記部屋に接続された側の端部と、該端部と対向する前記部屋の側面との間の距離は、
前記第2扁平伝熱管における前記部屋に接続された側の端部と、該端部と対向する前記部屋の側面との間の距離よりも短い請求項2~請求項8のいずれか一項に記載の冷凍サイクル装置。 - 前記冷凍サイクル回路に、エポキシ化合物が添加された冷凍機油が封入されている請求項9に記載の冷凍サイクル装置。
- 前記継手は、U字状配管である請求項1に記載の冷凍サイクル装置。
- 前記凹部は、下方に凹んでいる請求項11に記載の冷凍サイクル装置。
- 前記ハイドロフルオロオレフィン系冷媒は、2,3,3,3-テトラフルオロプロペン、1,3,3,3-テトラフルオロプロペン、及び1,1,2-トリフルオロエチレンであり、
前記2,3,3,3-テトラフルオロプロペン、前記1,3,3,3-テトラフルオロプロペン、及び前記1,1,2-トリフルオロエチレンのうちの少なくとも1つが前記冷凍サイクル回路に封入されている請求項1~請求項12のいずれか一項に記載の冷凍サイクル装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP15909744.3A EP3385643A4 (en) | 2015-12-01 | 2015-12-01 | Refrigeration cycle device |
PCT/JP2015/083751 WO2017094114A1 (ja) | 2015-12-01 | 2015-12-01 | 冷凍サイクル装置 |
CN201580084781.XA CN108291755B (zh) | 2015-12-01 | 2015-12-01 | 制冷循环装置 |
US15/764,899 US11105538B2 (en) | 2015-12-01 | 2015-12-01 | Refrigeration cycle apparatus |
JP2017553532A JP6529604B2 (ja) | 2015-12-01 | 2015-12-01 | 冷凍サイクル装置 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2015/083751 WO2017094114A1 (ja) | 2015-12-01 | 2015-12-01 | 冷凍サイクル装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2017094114A1 true WO2017094114A1 (ja) | 2017-06-08 |
Family
ID=58796568
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2015/083751 WO2017094114A1 (ja) | 2015-12-01 | 2015-12-01 | 冷凍サイクル装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US11105538B2 (ja) |
EP (1) | EP3385643A4 (ja) |
JP (1) | JP6529604B2 (ja) |
CN (1) | CN108291755B (ja) |
WO (1) | WO2017094114A1 (ja) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2017094114A1 (ja) * | 2015-12-01 | 2017-06-08 | 三菱電機株式会社 | 冷凍サイクル装置 |
KR102598605B1 (ko) * | 2019-01-29 | 2023-11-06 | 파이벨리 트랜스포트 라이프치히 게엠베하 앤 씨오. 케이지 | 가연성 냉매들을 위한 열 교환기 |
JP6881624B1 (ja) * | 2020-01-22 | 2021-06-02 | 株式会社富士通ゼネラル | 熱交換器 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0949671A (ja) * | 1995-05-29 | 1997-02-18 | Hitachi Ltd | 冷凍空調装置 |
JP2003302123A (ja) * | 2002-04-09 | 2003-10-24 | Mitsubishi Electric Corp | 熱交換器 |
KR20100060442A (ko) * | 2008-11-27 | 2010-06-07 | 주식회사 두원공조 | 냉매패스 대칭형 열교환기 |
JP2011085275A (ja) * | 2009-10-13 | 2011-04-28 | Panasonic Corp | 冷凍装置 |
JP2015055408A (ja) * | 2013-09-11 | 2015-03-23 | ダイキン工業株式会社 | 熱交換器及び空気調和機 |
WO2015046275A1 (ja) * | 2013-09-27 | 2015-04-02 | 三菱電機株式会社 | 熱交換器及びそれを用いた空気調和機 |
JP2015078833A (ja) * | 2013-09-11 | 2015-04-23 | ダイキン工業株式会社 | 熱交換器および空気調和機 |
Family Cites Families (52)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1470033A (en) * | 1921-05-06 | 1923-10-09 | Duriron Co | Radiator |
US3849854A (en) * | 1973-09-24 | 1974-11-26 | Emhart Corp | Method for making evaporator or condenser unit |
JP2558540B2 (ja) * | 1990-06-26 | 1996-11-27 | トヨタ自動車株式会社 | ポリプロピレン樹脂組成物 |
JPH04180801A (ja) * | 1990-11-15 | 1992-06-29 | Tanaka Kikinzoku Kogyo Kk | 溶媒抽出の連続運転方法 |
FR2673275B1 (fr) * | 1991-02-26 | 1994-01-07 | Valeo Thermique Moteur | Dispositif de raccordement d'un echangeur de chaleur, du type a serpentin, a une tubulure de circulation de fluide. |
JPH05195733A (ja) * | 1992-01-20 | 1993-08-03 | Isuzu Motors Ltd | 電磁駆動バルブ |
JPH0875320A (ja) | 1994-08-31 | 1996-03-19 | Sanyo Electric Co Ltd | 冷凍装置 |
JP3664511B2 (ja) * | 1994-12-27 | 2005-06-29 | 東芝キヤリア株式会社 | 冷媒、冷媒圧縮機および冷凍装置 |
US5810074A (en) * | 1996-09-13 | 1998-09-22 | American Standard Inc. | Serial heat exchanger and cascade circuitry |
JPH10300286A (ja) | 1996-11-25 | 1998-11-13 | Mitsubishi Electric Corp | スラッジ捕捉装置、その製造方法及びスラッジ捕捉装置を備えた冷凍空調機器 |
JP3342006B2 (ja) * | 2000-03-29 | 2002-11-05 | フタバ産業株式会社 | 偏芯拡管パイプの製造方法 |
JP4180801B2 (ja) * | 2001-01-11 | 2008-11-12 | 三菱電機株式会社 | 冷凍空調サイクル装置 |
DE10114300C1 (de) * | 2001-03-23 | 2002-10-31 | Uponor Innovation Ab | Fitting für den Anschluss eines Kunststoffrohres |
US6745827B2 (en) * | 2001-09-29 | 2004-06-08 | Halla Climate Control Corporation | Heat exchanger |
WO2003042611A1 (en) | 2001-11-15 | 2003-05-22 | Showa Denko K.K. | Heat exchanger, heat exchanger header tank and manufacturing method thereof |
JP4055449B2 (ja) * | 2002-03-27 | 2008-03-05 | 三菱電機株式会社 | 熱交換器およびこれを用いた空気調和機 |
US6722422B1 (en) * | 2003-06-10 | 2004-04-20 | Feldmeier Equipment, Inc. | Heat exchange system with improved flow velocity adjustment mechanism |
US7549465B2 (en) | 2006-04-25 | 2009-06-23 | Lennox International Inc. | Heat exchangers based on non-circular tubes with tube-endplate interface for joining tubes of disparate cross-sections |
FR2917819B1 (fr) * | 2007-06-22 | 2018-04-27 | Valeo Systemes Thermiques Branche Thermique Moteur | Module d'echange de chaleur pour deux circuits d'echange de chaleur |
US20100031505A1 (en) * | 2008-08-06 | 2010-02-11 | Oddi Frederick V | Cross-counterflow heat exchanger assembly |
US20120011863A1 (en) * | 2010-07-14 | 2012-01-19 | Honeywell International Inc. | Methods of servicing mobile air conditioning systems |
FR2950066B1 (fr) * | 2009-09-11 | 2011-10-28 | Arkema France | Refrigeration basse et moyenne temperature |
FR2950065B1 (fr) * | 2009-09-11 | 2012-02-03 | Arkema France | Fluide refrigerant binaire |
US8439104B2 (en) * | 2009-10-16 | 2013-05-14 | Johnson Controls Technology Company | Multichannel heat exchanger with improved flow distribution |
US9062236B2 (en) * | 2009-11-02 | 2015-06-23 | Arkema Inc. | Random copolymer oil return agents |
JP5195733B2 (ja) * | 2009-12-17 | 2013-05-15 | 三菱電機株式会社 | 熱交換器及びこれを備えた冷凍サイクル装置 |
JP2011226729A (ja) | 2010-04-22 | 2011-11-10 | Panasonic Corp | 冷凍装置 |
US8733619B2 (en) * | 2010-06-25 | 2014-05-27 | Arcelormittal Investigacion Y Desarrollo, S.L. | Nickel-base radiant tube and method for making the same |
EP3854860A1 (en) | 2011-05-19 | 2021-07-28 | Agc Inc. | Working medium and heat-cycle system |
JP5794022B2 (ja) | 2011-07-28 | 2015-10-14 | ダイキン工業株式会社 | 熱交換器 |
US9551540B2 (en) * | 2011-11-22 | 2017-01-24 | Daikin Industries, Ltd. | Heat exchanger |
CN104246415A (zh) * | 2011-12-06 | 2014-12-24 | 沙特阿拉伯石油公司 | 用于气冷热交换器的联管箱 |
WO2013160954A1 (ja) * | 2012-04-26 | 2013-10-31 | 三菱電機株式会社 | 熱交換器及びこの熱交換器を備えた冷凍サイクル装置 |
JP5609916B2 (ja) | 2012-04-27 | 2014-10-22 | ダイキン工業株式会社 | 熱交換器 |
JP5858478B2 (ja) * | 2012-09-04 | 2016-02-10 | シャープ株式会社 | パラレルフロー型熱交換器及びそれを搭載した空気調和機 |
US20150362222A1 (en) * | 2013-01-22 | 2015-12-17 | Mitsubishi Electric Corporation | Refrigerant distribution device and a heat pump apparatus using the same refrigerant distribution device |
CN111928678A (zh) * | 2013-03-15 | 2020-11-13 | 开利公司 | 用于风冷式冷却器的热交换器 |
GB2530915C (en) * | 2013-06-19 | 2019-10-30 | Mitsubishi Electric Corp | Air-conditioning apparatus |
CN105683639B (zh) | 2013-10-29 | 2018-01-19 | 三菱电机株式会社 | 管接头、换热器和空调装置 |
CN105683701A (zh) | 2013-10-29 | 2016-06-15 | 三菱电机株式会社 | 换热器和空调装置 |
KR20150094954A (ko) * | 2014-02-12 | 2015-08-20 | 엘지전자 주식회사 | 열교환기 |
US10605502B2 (en) * | 2014-10-07 | 2020-03-31 | Mitsubishi Electric Corporation | Heat exchanger and air-conditioning apparatus |
JP6333401B2 (ja) * | 2014-10-07 | 2018-05-30 | 三菱電機株式会社 | 熱交換器、及び、空気調和装置 |
JP5987889B2 (ja) * | 2014-11-14 | 2016-09-07 | ダイキン工業株式会社 | 熱交換器 |
US10231357B2 (en) * | 2015-03-20 | 2019-03-12 | International Business Machines Corporation | Two-phase cooling with ambient cooled condensor |
JP6641721B2 (ja) * | 2015-04-27 | 2020-02-05 | ダイキン工業株式会社 | 熱交換器および空気調和機 |
WO2017094114A1 (ja) * | 2015-12-01 | 2017-06-08 | 三菱電機株式会社 | 冷凍サイクル装置 |
WO2017109933A1 (ja) * | 2015-12-25 | 2017-06-29 | 三菱電機株式会社 | 熱交換器、これを備えた空気調和機、及び扁平管uベンドの製造方法 |
CN109073290B (zh) * | 2016-05-19 | 2020-10-30 | 三菱电机株式会社 | 室外单元及具备该室外单元的制冷循环装置 |
WO2018003121A1 (ja) * | 2016-07-01 | 2018-01-04 | 三菱電機株式会社 | 熱交換器およびこの熱交換器を備えた冷凍サイクル装置 |
JP6746234B2 (ja) * | 2017-01-25 | 2020-08-26 | 日立ジョンソンコントロールズ空調株式会社 | 熱交換器、及び、空気調和機 |
TWI677659B (zh) * | 2019-01-16 | 2019-11-21 | 萬在工業股份有限公司 | 並聯式冷凝裝置 |
-
2015
- 2015-12-01 WO PCT/JP2015/083751 patent/WO2017094114A1/ja active Application Filing
- 2015-12-01 US US15/764,899 patent/US11105538B2/en active Active
- 2015-12-01 JP JP2017553532A patent/JP6529604B2/ja active Active
- 2015-12-01 CN CN201580084781.XA patent/CN108291755B/zh active Active
- 2015-12-01 EP EP15909744.3A patent/EP3385643A4/en active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0949671A (ja) * | 1995-05-29 | 1997-02-18 | Hitachi Ltd | 冷凍空調装置 |
JP2003302123A (ja) * | 2002-04-09 | 2003-10-24 | Mitsubishi Electric Corp | 熱交換器 |
KR20100060442A (ko) * | 2008-11-27 | 2010-06-07 | 주식회사 두원공조 | 냉매패스 대칭형 열교환기 |
JP2011085275A (ja) * | 2009-10-13 | 2011-04-28 | Panasonic Corp | 冷凍装置 |
JP2015055408A (ja) * | 2013-09-11 | 2015-03-23 | ダイキン工業株式会社 | 熱交換器及び空気調和機 |
JP2015078833A (ja) * | 2013-09-11 | 2015-04-23 | ダイキン工業株式会社 | 熱交換器および空気調和機 |
WO2015046275A1 (ja) * | 2013-09-27 | 2015-04-02 | 三菱電機株式会社 | 熱交換器及びそれを用いた空気調和機 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3385643A4 * |
Also Published As
Publication number | Publication date |
---|---|
JPWO2017094114A1 (ja) | 2018-07-12 |
EP3385643A4 (en) | 2018-12-05 |
JP6529604B2 (ja) | 2019-06-12 |
EP3385643A1 (en) | 2018-10-10 |
US20180274820A1 (en) | 2018-09-27 |
US11105538B2 (en) | 2021-08-31 |
CN108291755B (zh) | 2020-07-31 |
CN108291755A (zh) | 2018-07-17 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
KR101166806B1 (ko) | 이중관 및 이를 구비한 열교환기 | |
KR101249721B1 (ko) | 열교환용 이중관 | |
EP1944562B1 (en) | Air conditioner | |
CN104024782B (zh) | 热交换器和冷冻装置 | |
EP2752627B1 (en) | Refrigeration device | |
US20130199765A1 (en) | Air conditioner | |
JP6351875B1 (ja) | 熱交換器及び冷凍サイクル装置 | |
JP2008281326A (ja) | 冷凍装置及び該冷凍装置に用いる熱交換器 | |
WO2017094114A1 (ja) | 冷凍サイクル装置 | |
KR20170109462A (ko) | 대체냉매적용 공조시스템의 내부 열교환기 이중관 구조 | |
EP4155646A1 (en) | Heat exchanger, outdoor unit, and refrigeration cycle device | |
US11105521B2 (en) | Outdoor unit | |
JP2001124442A (ja) | アキューム・レシーバおよびその製造方法 | |
JP2009300001A (ja) | 冷凍サイクル装置 | |
EP4116642A1 (en) | Heat exchanger and air conditioner | |
CN113544458B (zh) | 气体集管、热交换器以及制冷循环装置 | |
JP2016148483A (ja) | 冷凍装置 | |
EP3699539B1 (en) | Heat exchanger and air conditioning device with same | |
WO2016117447A1 (ja) | 空気調和装置 | |
JP7418551B2 (ja) | 熱交換器、室外機、および空気調和装置 | |
JPWO2018163727A1 (ja) | 冷凍装置 | |
JP2013139943A (ja) | 熱交換器 | |
KR101397944B1 (ko) | 효율이 우수한 이중관식열교환기를 갖는 단단압축 방식의 냉동기 | |
US11506431B2 (en) | Refrigeration cycle apparatus | |
US11054187B2 (en) | Heat exchanger and method of manufacturing same |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 15909744 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2017553532 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15764899 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2015909744 Country of ref document: EP |