WO2020084786A1 - Échangeur de chaleur et dispositif à cycle frigorifique faisant appel audit échangeur - Google Patents

Échangeur de chaleur et dispositif à cycle frigorifique faisant appel audit échangeur Download PDF

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Publication number
WO2020084786A1
WO2020084786A1 PCT/JP2018/039965 JP2018039965W WO2020084786A1 WO 2020084786 A1 WO2020084786 A1 WO 2020084786A1 JP 2018039965 W JP2018039965 W JP 2018039965W WO 2020084786 A1 WO2020084786 A1 WO 2020084786A1
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Prior art keywords
heat exchanger
fins
heat transfer
region
longitudinal direction
Prior art date
Application number
PCT/JP2018/039965
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English (en)
Japanese (ja)
Inventor
綾 河島
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2020552495A priority Critical patent/JP7112053B2/ja
Priority to CN201890000662.0U priority patent/CN211290633U/zh
Priority to PCT/JP2018/039965 priority patent/WO2020084786A1/fr
Publication of WO2020084786A1 publication Critical patent/WO2020084786A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements

Definitions

  • the present invention relates to a heat exchanger and a refrigeration cycle device using the heat exchanger.
  • a plurality of plate-shaped fins arranged so as to be stacked at a preset interval, and a plurality of heat transfer tubes penetrating along the direction in which these fins are arranged in parallel
  • a fin-and-tube type heat exchanger having
  • the heat transfer tubes used in such heat exchangers have, for example, a perfect circular cross section or a flat shape such as an elliptical shape or an oval shape.
  • a plurality of openings such as through holes or notches corresponding to the shape of the heat transfer tube are formed in the plurality of fins, and the heat transfer tube is inserted into these openings.
  • the plurality of heat transfer tubes are assembled with the fins penetrating along the direction in which the fins are arranged in parallel.
  • fins are formed with fin collars that are cut and raised perpendicularly to the heat transfer tubes, and the fin collars are brazed in the furnace or adhered to the heat transfer tubes by using an adhesive to form heat transfer tubes. Adhesion with the fin can be improved.
  • each heat transfer tube is connected to a distribution pipe or header that forms a refrigerant flow path together with the heat transfer tube. Then, in the heat exchanger, heat is exchanged between the heat exchange fluid such as air or gas flowing between the fins and the heat exchanged fluid such as water or refrigerant flowing in the heat transfer tube.
  • the heat exchange fluid such as air or gas flowing between the fins
  • the heat exchanged fluid such as water or refrigerant flowing in the heat transfer tube.
  • a heat exchanger in which a cut-and-raised part called a slit or a louver that opens in the direction in which air mainly flows is formed, or a scratch or a waffle that protrudes in the direction in which air mainly flows.
  • Heat exchangers are known in which so-called protrusions are formed.
  • the cut-and-raised portion or the protruding portion is provided to increase the surface area for heat exchange, thereby improving the heat exchange performance.
  • heat exchangers in which a plurality of flow paths are formed inside the heat transfer tube, or heat exchangers in which grooves are formed on the inner surface of the heat transfer tube are known. Even in such a heat exchanger, the heat exchange performance is improved by providing a plurality of flow paths or grooves to increase the surface area for heat exchange.
  • the heat exchanger when the heat exchanger is installed in an outdoor unit and used as an evaporator, water in the air becomes frost and adheres to the heat exchanger. Therefore, in an air conditioner or a refrigerator including a heat exchanger, the frost adhering to the heat exchanger is melted by performing a defrosting operation, and the frost that has been melted into water droplets is removed from the surface of the fins and the heat transfer tubes. Then, it is hung down in the longitudinal direction and discharged below the heat exchanger.
  • Patent Document 1 a heat exchanger is proposed in which the entire fin region except for the annular portion formed around the insertion hole through which the heat transfer tube is inserted has a wave shape including peaks and valleys extending in the vertical direction. There is.
  • the present invention is to solve the above-mentioned problems, and even if the heat transfer tube has a flat shape, it is possible to improve the heat exchange performance while ensuring drainage, and a heat exchanger using the same. It is an object of the present invention to provide a refrigeration cycle device that has been used.
  • a heat exchanger according to the present invention and a refrigeration cycle apparatus using the heat exchanger are inserted into a plurality of plate-shaped fins arranged side by side in a front-back direction at preset intervals, and insertion holes formed in the fins.
  • a plurality of heat transfer tubes each having a flat cross section and arranged side by side in the longitudinal direction of the fins at predetermined intervals with respect to the fins, and the heat transfer tubes retain hydrophilicity on the outer peripheral surface.
  • the fin has an uneven shape provided adjacent to each other in the lateral direction orthogonal to the longitudinal direction, has a groove portion extending in the longitudinal direction, and retains hydrophilicity. It has been processed.
  • the heat exchanger and the refrigeration cycle apparatus using the same by collecting the water droplets adhering to the fin surface in the groove portion of the fin, the water droplet can be promptly guided downward in the longitudinal direction to be drained. it can.
  • the water droplets that have accumulated on the upper surface of the heat transfer tube wet and spread, so that even with a flat heat transfer tube, the water droplets can be guided downward in the longitudinal direction and drained without water droplets accumulating on the upper surface of the heat transfer tube.
  • the water droplets on the fin surface can be quickly and surely drained, and thus the heat exchange performance can be improved while ensuring drainage. .
  • FIG. 4 is a sectional view showing an AA section of FIG. 3.
  • FIG. 3 is a perspective view illustrating a main part of the outdoor heat exchanger of FIG. 2, which is used for explaining a step of inserting a heat transfer tube and fins.
  • 5 is an enlarged view of a main part of the heat exchanger according to Comparative Example 1.
  • FIG. 5 is an enlarged view of a main part showing water droplets on the surface of the heat exchanger according to Comparative Example 1.
  • FIG. 6 is an enlarged view of a main part of a heat exchanger according to Comparative Example 2.
  • FIG. 6 is an enlarged view of a main part showing drainage of water droplets on the surface of the heat exchanger according to Comparative Example 2.
  • FIG. 3 is an enlarged view of a main part showing drainage of water droplets on the surface of the heat exchanger according to the first embodiment. It is a principal part enlarged view of the heat exchanger which concerns on Embodiment 2 of this invention. It is sectional drawing which shows the BB cross section of FIG. It is a principal part enlarged view in the heat exchanger of FIG.
  • FIG. 17 is a cross-sectional view showing a CC cross section of FIG. 16. It is a principal part enlarged view which shows the drainage of the water droplet of the surface in the heat exchanger which concerns on Embodiment 3 of this invention. It is a principal part enlarged view which shows the drainage of the water droplet of the surface in the heat exchanger which concerns on Embodiment 3 of this invention.
  • FIG. 1 is a refrigerant circuit diagram showing an example of a refrigeration cycle device according to Embodiment 1 of the present invention.
  • the flow of the refrigerant during the cooling operation is indicated by a dashed arrow
  • the flow of the refrigerant during the heating operation is indicated by a solid arrow.
  • the refrigeration cycle apparatus 1 includes a compressor 2, a four-way valve 3, an indoor heat exchanger 4, an indoor fan 5, an expansion device 6, an outdoor fan 7, and an outdoor heat exchanger 10.
  • the compressor 2, the four-way valve 3, the indoor heat exchanger 4, the expansion device 6, and the outdoor heat exchanger 10 are connected by a refrigerant pipe to form a refrigerant circuit.
  • the compressor 2 compresses the refrigerant.
  • the refrigerant compressed by the compressor 2 is discharged and sent to the four-way valve 3.
  • the compressor 2 can be configured by, for example, a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor, or the like.
  • the indoor heat exchanger 4 functions as a condenser during heating operation and as an evaporator during cooling operation.
  • the indoor heat exchanger 4 is, for example, a fin-and-tube heat exchanger, a microchannel heat exchanger, a shell-and-tube heat exchanger, a heat pipe heat exchanger, a double-tube heat exchanger, or a plate heat exchanger. It can be configured with a container or the like.
  • the expansion device 6 expands and decompresses the refrigerant that has passed through the indoor heat exchanger 4 or the outdoor heat exchanger 10.
  • the expansion device 6 can be composed of, for example, an electric expansion valve capable of adjusting the flow rate of the refrigerant.
  • an electric expansion valve capable of adjusting the flow rate of the refrigerant.
  • a mechanical expansion valve having a diaphragm as a pressure receiving portion, a capillary tube, or the like can be applied.
  • the outdoor heat exchanger 10 functions as an evaporator during heating operation and as a condenser during cooling operation.
  • the outdoor heat exchanger 10 will be described in detail later.
  • the four-way valve 3 switches the flow of refrigerant between heating operation and cooling operation. That is, the four-way valve 3 connects the discharge port of the compressor 2 to the indoor heat exchanger 4 and the refrigerant flow so as to connect the suction port of the compressor 2 to the outdoor heat exchanger 10 during the heating operation. Switch. Further, the four-way valve 3 connects the discharge port of the compressor 2 with the outdoor heat exchanger 10 and the refrigerant flow so as to connect the suction port of the compressor 2 with the indoor heat exchanger 4 during the cooling operation. Switch.
  • the indoor fan 5 is attached to the indoor heat exchanger 4 and supplies air, which is a heat exchange fluid, to the indoor heat exchanger 4.
  • the outdoor fan 7 is attached to the outdoor heat exchanger 10 and supplies air as a heat exchange fluid to the outdoor heat exchanger 10.
  • the high-temperature and high-pressure gas-state refrigerant is discharged from the compressor 2.
  • the refrigerant flows according to the broken line arrow.
  • the high-temperature and high-pressure gas refrigerant (single phase) discharged from the compressor 2 flows into the outdoor heat exchanger 10 functioning as a condenser via the four-way valve 3.
  • the outdoor heat exchanger 10 heat is exchanged between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the outdoor fan 7, the high-temperature and high-pressure gas refrigerant is condensed, and the high-pressure liquid refrigerant (single Phase).
  • the high-pressure liquid refrigerant sent from the outdoor heat exchanger 10 becomes a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant by the expansion device 6.
  • the two-phase state refrigerant flows into the indoor heat exchanger 4 that functions as an evaporator.
  • the indoor heat exchanger 4 heat is exchanged between the two-phase state refrigerant that has flowed in and the air supplied by the indoor fan 5, and the liquid refrigerant of the two-phase state refrigerant evaporates to form a low-pressure gas. It becomes a refrigerant (single phase). Due to this heat exchange, the inside of the room is cooled.
  • the low-pressure gas refrigerant sent from the indoor heat exchanger 4 flows into the compressor 2 via the four-way valve 3, is compressed into a high-temperature high-pressure gas refrigerant, and is discharged from the compressor 2 again. Hereinafter, this cycle is repeated.
  • the compressor 2 As shown in FIG. 1, by driving the compressor 2, the high-temperature and high-pressure gas-state refrigerant is discharged from the compressor 2. Hereafter, the refrigerant flows according to the solid arrow.
  • the indoor heat exchanger 4 heat is exchanged between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the indoor fan 5, and the high-temperature and high-pressure gas refrigerant is condensed to form a high-pressure liquid refrigerant (single-phase). )become.
  • the heat exchange heats the room.
  • the high-pressure liquid refrigerant sent from the indoor heat exchanger 4 becomes a two-phase refrigerant of low-pressure gas refrigerant and liquid refrigerant by the expansion device 6.
  • the two-phase refrigerant flows into the outdoor heat exchanger 10 that functions as an evaporator.
  • heat exchange is performed between the two-phase refrigerant that has flowed in and the air supplied by the outdoor fan 7, and the liquid refrigerant of the two-phase refrigerant evaporates to form a low-pressure gas. It becomes a refrigerant (single phase).
  • the low-pressure gas refrigerant sent from the outdoor heat exchanger 10 flows into the compressor 2 via the four-way valve 3, is compressed into a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 2 again. Hereinafter, this cycle is repeated.
  • the refrigerant flowing out from the indoor heat exchanger 4 during the cooling operation or the outdoor heat exchanger 10 during the heating operation is a gas refrigerant (single phase).
  • the evaporator when heat exchange is performed between the air supplied from the fan and the refrigerant flowing inside the heat transfer tube forming the evaporator, water in the air is condensed and evaporated. Water drops form on the surface of the vessel. The water droplets generated on the surface of the evaporator travel along the surfaces of the fins and the heat transfer tubes and are dropped downward, and are discharged as drain water below the evaporator.
  • the refrigeration cycle apparatus 1 performs the “defrosting operation” for removing frost when the outside air has a certain temperature (for example, 0 ° C.) or less.
  • the "defrosting operation” is to supply hot gas (high-temperature high-pressure gas refrigerant) from the compressor 2 to the outdoor heat exchanger 10 in order to prevent frost from adhering to the outdoor heat exchanger 10 that functions as an evaporator. It is driving.
  • the defrosting operation may be executed when the duration of the heating operation reaches a predetermined value (for example, 30 minutes). In addition, the defrosting operation may be performed before the heating operation when the outdoor heat exchanger 10 has a constant temperature (for example, -6 ° C) or less. The frost and ice attached to the outdoor heat exchanger 10 are melted by the hot gas supplied to the outdoor heat exchanger 10 during the defrosting operation.
  • a bypass refrigerant pipe (not shown) is provided between the outlet of the compressor 2 and the outdoor heat exchanger 10 so that hot gas can be directly supplied from the compressor 2 to the outdoor heat exchanger 10 during the defrosting operation. ) May be used for connection.
  • the discharge port of the compressor 2 is connected to the outdoor heat exchanger 10 via a refrigerant flow path switching device (for example, a four-way valve 3) so that hot gas can be supplied from the compressor 2 to the outdoor heat exchanger 10. It may be configured to.
  • FIG. 2 is a perspective view showing an example of the outdoor heat exchanger in the refrigeration cycle device according to Embodiment 1 of the present invention.
  • FIG. 3 is an enlarged view of a main part of the outdoor heat exchanger of FIG.
  • FIG. 4 is a sectional view showing an AA section of FIG.
  • FIG. 5 is a perspective view showing a main part of the outdoor heat exchanger of FIG. 2 and is used for explaining a step of inserting the heat transfer tubes and the fins.
  • the x direction is the depth direction of the outdoor heat exchanger 10, and indicates the width direction that is short in the fins 11 of the outdoor heat exchanger 10.
  • the y direction is the width direction of the outdoor heat exchanger 10, and shows the direction in which the fins 11 that are the depth (thickness) direction in the fins 11 are arranged in parallel.
  • the z direction is the longitudinal direction (vertical direction) of the outdoor heat exchanger 10, and represents the height direction of the fins 11.
  • the white arrow K represents the ventilation direction of the air supplied from the outdoor fan 7 to the outdoor heat exchanger 10.
  • the outdoor heat exchanger 10 according to the first embodiment is supplied with air from the outdoor fan 7 shown in FIG. 1 in the ventilation direction K (x direction of the fins 11).
  • FIG. 3 shows a main part when the outdoor heat exchanger 10 is observed in the y direction.
  • FIG. 4 shows an AA cross section in the fin 11 of FIG.
  • the outdoor heat exchanger 10 is, for example, a two-row structure heat exchanger, and includes a windward heat exchanger 10A and a leeward heat exchanger 10B.
  • the windward side heat exchanger 10A and the leeward side heat exchanger 10B are fin-and-tube type heat exchangers, and the ventilation direction K of the air supplied from the outdoor fan 7 shown in FIG. 1, that is, the outdoor heat exchanger 10 is shown.
  • the windward side heat exchanger 10A is arranged on the windward side in the ventilation direction K of the air supplied from the outdoor fan 7, and the leeward side heat exchanger 10B is the leeward side in the ventilation direction K of the air supplied from the outdoor fan 7. It is located in.
  • One end of the heat transfer pipe 12 of the windward heat exchanger 10A is connected to the windward header collecting pipe 10C.
  • One end of the heat transfer pipe 12 of the leeward heat exchanger 10B is connected to the leeward header collecting pipe 10D.
  • the other end of the heat transfer tube 12 of the windward heat exchanger 10A and the other end of the heat transfer tube 12 of the leeward heat exchanger 10B are connected to the inter-row connection member 10E.
  • one of the windward heat exchanger 10A and the leeward heat exchanger 10B is transferred from one of the windward header collecting pipe 10C and the leeward header collecting pipe 10D.
  • the refrigerant is distributed to the heat pipe 12.
  • the refrigerant distributed to the one heat transfer tube 12 of the upwind heat exchanger 10A or the downwind heat exchanger 10B passes through the inter-row connection member 10E, and the downwind heat exchanger 10B or the upwind heat exchanger 10A. Flows into the other heat transfer tube 12.
  • the refrigerant flowing into the other heat transfer pipe 12 of the leeward heat exchanger 10B or the windward heat exchanger 10A merges with the other of the leeward header collecting pipe 10D or the leeward header collecting pipe 10C, and the compressor 2 It flows toward the suction port or the throttling device 6.
  • the windward heat exchanger 10A and the leeward heat exchanger 10B have the same configuration. Therefore, the windward heat exchanger 10A will be described below as a representative of both.
  • the windward heat exchanger 10A and the leeward heat exchanger 10B are simply referred to as the heat exchanger 13.
  • the heat exchanger 10 may be configured.
  • the heat exchanger 13 includes a plurality of fins 11 and a plurality of heat transfer tubes 12.
  • the fins 11 are rectangular plate-shaped members extending in the longitudinal direction (z direction), and as shown in FIG. 5, the fins 11 are arranged in the same outdoor heat exchanger 10 in the front-back direction at predetermined intervals. It is arranged. In the case of the first embodiment, the fins 11 are arranged in the same outdoor heat exchanger 10 side by side in the y direction at a prescribed fin pitch interval FP.
  • a plurality of insertion holes 14 into which the heat transfer tubes 12 are inserted are formed in the fins 11 above and below in the longitudinal direction of the fins 11 at predetermined intervals.
  • the fin 11 has a plurality of concavo-convex shapes provided adjacent to each other along the ventilation direction K of the air from the outdoor fan 7 in a region excluding the insertion holes 14, and has a groove portion 15 extending in the longitudinal direction.
  • the region excluding the insertion hole 14 of the fin 11 is the entire region excluding the insertion hole 14 including the first region P where the insertion hole 14 does not exist in the longitudinal direction.
  • the air flow direction K of the air from the outdoor fan 7 indicates the same direction as the x direction as the lateral direction orthogonal to the z direction as the longitudinal direction.
  • the uneven space RSm is preferably 5 mm or less. This is because, as a result of the study, it is clear that when the diameter of the water droplets is about 5 mm, the water droplets are dropped in the longitudinal direction by its own weight, and the effect of aggregating the water droplets due to the uneven shape is expected to be 5 mm or less. Further, the unevenness height Ra is preferably about 1/3 of the fin pitch interval FP (FIG. 5) in order to prevent the fins from contacting each other.
  • Such a concavo-convex shape can be formed by a method of imparting a concavo-convex shape to a press or rolling roll and transferring the roll.
  • a cut-and-raised portion or a protruding portion may be further formed to increase the surface area for heat exchange and improve the heat exchange performance.
  • FIGS. 3 and 5 two heat transfer tubes 12 located above and below in the z direction are shown as representatives. As shown in FIG. 3, the upper heat transfer tube 12 and the lower heat transfer tube 12 are inserted into the insertion holes 14 formed in the fin 11, and the length of the fin 11 is increased at predetermined intervals with respect to the fin 11. They are arranged side by side.
  • the heat transfer tube 12 extends in the y direction, which is the direction in which the plurality of fins 11 are arranged in parallel, and the end portions of the insertion holes 14 formed in the plurality of fins 11 are formed. 14a is inserted in the x direction. Thereby, the plurality of fins 11 hold the heat transfer tube 12 in a state where the heat transfer tube 12 penetrates the insertion hole 14.
  • the heat transfer tube 12 is a flat tube whose cross section orthogonal to the longitudinal direction has a flat shape.
  • the fins 11 and the heat transfer tubes 12 according to the first embodiment are subjected to a treatment for keeping their surfaces hydrophilic.
  • the contact angle between the surfaces of the fins 11 and the heat transfer tubes 12 is preferably 30 ° or less. Further, it is desirable that the fins 11 have higher hydrophilicity than the heat transfer tubes 12.
  • the surface of the fins 11 and the heat transfer tubes 12 is made hydrophilic by post-coating with a flux or a hydrophilic agent used when brazing the fins 11 and the heat transfer tubes 12. A conductive coating can be formed.
  • FIG. 6 is an enlarged view of a main part of the heat exchanger 100 according to Comparative Example 1.
  • the contact angle between the surfaces of the fin 101 and the heat transfer tube 102 of Comparative Example 1 is about 80 °.
  • the heat exchanger 100 is different from the heat exchanger 13 according to the first embodiment in that the heat exchanger 100 does not have the groove portion 15 formed on the surface of the fin 11 shown in FIG. It is not hydrophilic.
  • 7: is a principal part enlarged view which shows the water droplet of the surface of the heat exchanger 100 which concerns on the comparative example 1.
  • FIG. 8 is an enlarged view of a main part of the heat exchanger 110 according to Comparative Example 2.
  • FIG. 9 is an enlarged view of an essential part showing drainage of water droplets on the surface of the heat exchanger 110 according to Comparative Example 2.
  • the contact angle between the surfaces of the fin 111 and the heat transfer tube 112 of Comparative Example 2 is about 10 °.
  • the heat exchanger 110 is different from the heat exchanger 13 according to the first embodiment in that it does not have the groove portion 15 formed on the surface of the fin 11 shown in FIG. 3. In the heat exchanger 110 of Comparative Example 2, as shown in FIG.
  • the water droplet H is drained to the lower side of the heat exchanger 110 by repeating the draining process of flowing to the lower surface of the heat transfer tube 112 along the outer peripheral surface of the heat transfer tube 112 (FIG. 9). Therefore, although it takes time, the residual water in the heat exchanger 110 can be made smaller than that in Comparative Example 1.
  • the water droplets H on the upper surface of the heat transfer tube 112 wet and spread along the outer peripheral surface of the heat transfer tube 112 to the lower surface "whole area" of the heat transfer tube 112, and are further drained to the upper surface "whole area” of the heat transfer tube 112. Therefore, the drainage path is longer than that of the heat exchanger 13 of the first embodiment described later, and it takes time to drain the heat exchanger 110 below the heat exchanger 110.
  • the surfaces of the fins 11 and the heat transfer tubes 12 are each hydrophilic, the water droplets H collected on the upper surface of the heat transfer tubes 12 spread along the outer peripheral surface of the heat transfer tubes 12 without accumulating on the upper surfaces of the heat transfer tubes 12. . Then, the water droplets H are guided to the groove portion 15 by the hydrophilic property of the fins 11 and then drained downward along the groove portion 15 in the longitudinal direction.
  • FIG. 10 is an enlarged view of an essential part showing drainage of water droplets on the surface of the heat exchanger according to the first embodiment. Since the insertion hole 14 is formed in a region of the fin 11 where the heat transfer tube 12 exists in the longitudinal direction, the groove portion 15 is cut off at the position of the insertion hole 14.
  • the water droplets H attached to the surfaces of the fins 11 can be collected in the groove portions 15 and quickly drained downward in the longitudinal direction of the heat exchanger 13. it can. Further, by allowing the water droplets H accumulated on the upper surface of the heat transfer tube 12 to spread, the water droplets H do not accumulate on the upper surface of the heat transfer tube 12 even if the heat transfer tube 12 has a flat shape, and the water droplets H move downward in the longitudinal direction. It can be led to and drained.
  • the water droplets H accumulated on the upper surface of the heat transfer tube 12 can be mainly drained in the first region P where drainage is easy in the longitudinal direction of the fin 11 without the insertion hole 14. Therefore, the condensed water of the entire heat exchanger 13 or the water droplets H such as dissolved water due to the defrosting operation can be drained much more rapidly. Therefore, even in the heat exchanger 13 using the flat heat transfer tube 12, the water droplets H on the surfaces of the fins 11 can be quickly and surely drained, thus improving drainage and heat exchange performance. Can be planned.
  • Embodiment 2 Next, a refrigeration cycle apparatus 1 (FIG. 1) according to Embodiment 2 of the present invention will be described. Specifically, in the above-described first embodiment, the case where the groove portion 15 is provided on the entire surface of the fin 11 in the x direction has been described (see FIGS. 3 to 5, 10 and the like). On the other hand, in the refrigeration cycle apparatus 1 according to the second embodiment, as shown in FIG. 11 described later, the fins 21 of the heat exchanger 20 have different regions in which the groove portions 25 extending in the longitudinal direction are provided, The other configurations are the same. For this reason, in the second embodiment, a specific configuration of the heat exchanger 20 will be described, and other redundant description will be omitted.
  • FIG. 11 is an enlarged view of a main part of the heat exchanger 20 according to Embodiment 2 of the present invention.
  • FIG. 12 is a cross-sectional view showing a BB cross section of FIG.
  • FIG. 13 is an enlarged view of a main part of the heat exchanger 20 of FIG.
  • the groove portion 25 is provided in the area where the heat transfer tube 22 (insertion hole 24) does not exist in the z direction on the surface of the fin 21.
  • the fin 21 is located on the first region P where the insertion hole 24 does not exist in the longitudinal direction and on the center side in the lateral direction of the first region P in the longitudinal direction, and in the lateral direction of the insertion hole 24.
  • the groove portion 25 is provided in the second region Q including the end portion 24a on the side of the first region P in.
  • the second region Q includes the vicinity of the boundary between the groove 24 and the end 24 a of the heat transfer tube 22 on the first region P side in the insertion hole 24.
  • the second region Q has an RSm of RSm from the end 24a on the first region P side of the insertion hole 24 toward the center side of the insertion hole 24 in the lateral direction. It is desirable that the area is twice as wide.
  • the second area Q is an area having a width twice as large as RSm from the end portion 24a on the first area P side of the insertion hole 24 toward the center side of the insertion hole 24 in the lateral direction. This is to secure the groove portion 25 that functions as a drainage path for the water droplets H attached to the upper surface of the.
  • a width of one RSm corresponds to either a concave portion or a convex portion of the unevenness forming the groove 25, and makes the groove function as a drainage path for the water droplets H attached to the upper surface of the heat transfer tube 22. 25 cannot always be secured. Therefore, by making the region twice the width of RSm, it is possible to surely hold the groove portion 25 that has both the concave and convex shapes that form the groove portion 25 and that functions as the drainage path of the water droplets H.
  • the same effect as that of the first embodiment can be obtained by only providing the groove portion 25 extending in the longitudinal direction only in the first region P and the second region Q. Obtainable. That is, in the heat exchanger 20 according to the second embodiment, the water droplets H accumulated on the surfaces of the fins 21 and the upper surfaces of the heat transfer tubes 22 are moved downward in the longitudinal direction via the groove portions 25 of the first region P and the second region Q. It is possible to drain water quickly and surely. Therefore, not only the heat exchange performance can be improved while ensuring the drainage property of the heat exchanger 20, but the formation region of the groove 25 in the fin 21 can be reduced to simplify the configuration.
  • FIG. 14 is an enlarged view of a main part in the first modification of the heat exchanger 20 according to the second embodiment of the present invention.
  • a third region R which is on the center side in the lateral direction with respect to the second region Q and is a flat face in which the insertion hole 24 exists in the longitudinal direction of the fin 21, projects from the flat face.
  • the cut-and-raised portion 26, the protruding portion 27, or both may be provided. In this case, the heat exchange performance can be further improved by increasing the surface area of the fin 21 for heat exchange.
  • the opposite end of the end 24a on the first region P side in the insertion hole 24 is formed in a notched state.
  • the present invention is not limited to this.
  • FIG. 15 is an enlarged view of a main part in the second modification of the heat exchanger 20 according to the second embodiment of the present invention.
  • the end portion on the opposite side of the end portion 24a on the first region P side of the insertion hole 240 formed in the fin 210 may not be in the notched state.
  • the fin 210 of the heat exchanger 200 has an insertion hole 240 corresponding to the heat transfer tube 220 opened at the center of the fin 210.
  • the insertion hole 240 includes an end portion 240a on the first region T side located upstream of the air ventilation direction K and an opposite end portion 240b located downstream of the air ventilation direction K opposite thereto.
  • the region corresponding to the first region P is the first region T
  • the region corresponding to the second region Q is the second region U
  • the region corresponding to the third region R is the third region V
  • the holes 240 are formed symmetrically in the lateral direction around the hole 240.
  • the heat exchanger 200 like the heat exchanger 20 described above, water droplets (not shown) accumulated on the surfaces of the fins 210 and the upper surfaces of the heat transfer tubes 220 are formed in the groove portions of the first region T and the second region U.
  • the groove 250 is not provided in the entire area of the surface of the fin 210 in the x direction, but is provided in the first region T and the second region U to the minimum necessary. Can be simplified.
  • the insertion hole 240 is opened in the center of the fin 210 in a flat shape corresponding to the heat transfer tube 220 without notching the opposite end portion 240b, it is remarkably compared with the case having the notch.
  • the heat transfer tube 220 can be stably held.
  • Embodiment 3 Next, a refrigeration cycle apparatus 1 (FIG. 1) according to Embodiment 3 of the present invention will be described. Specifically, in the above-described first embodiment, the case where the extending direction of the groove portion 15 on the surface of the fin 11 is parallel to the upper and lower sides in the longitudinal direction has been described (see FIGS. 3 to 5, 10 and the like). On the other hand, in the refrigeration cycle apparatus 1 according to the third embodiment, as shown in FIGS. 16 to 19 described later, the extending direction of the groove 35 in the fin 31 of the heat exchanger 30 is the longitudinal direction of the fin 31. Other than that the point is inclined with respect to the direction, the others are configured similarly.
  • the region corresponding to the first region P in the above-described first embodiment is the first region Pa, and the end portion 14a of the insertion hole 14 on the first region P side is the first region Pa side in the insertion hole 34. End portion 34a.
  • FIG. 16 is an enlarged view of a main part of the heat exchanger 30 according to the third embodiment of the present invention.
  • FIG. 17 is a cross-sectional view showing a CC cross section of FIG.
  • the groove portion 35 in the heat exchanger 30 of the third embodiment, in the z direction on the surface of the fin 31, when the groove portion 35 is arranged with the longitudinal direction facing up and down in the gravity direction, the groove portion is arranged.
  • the inclining direction of 35 inclines downward toward the first region Pa.
  • the groove portion 35 extends in a state in which the groove 35 is inclined in the downward direction opposite to the ventilation direction K of the air flowing between the fins 31. .
  • FIG. 18 is an enlarged view of an essential part showing drainage of water droplets on the surface of the heat exchanger 30 according to the third embodiment of the present invention.
  • FIG. 19 is an enlarged view of an essential part showing drainage of water droplets on the surface of the heat exchanger 30 according to Embodiment 3 of the present invention.
  • the water droplets H accumulated on the upper surface of the heat transfer tube 32 in the insertion hole 34 spread wet along the outer peripheral surface of the hydrophilic heat transfer tube 32, and the heat transfer tube 32.
  • the water is drained along the groove 35A on the surface of the fin 31 that first intersects with the upper drainage path.
  • the groove portion 35A extends toward the end of the fin 31 on the side of the first region Pa, the drained water droplet H does not come into contact with the heat transfer pipe 32 below and the first region Pa where drainage is easy. Be led up to.
  • each groove 35 is arranged such that the height position of the one groove 35 on the surface of the fin 31 on the first region Pa side where the heat transfer tube 32 does not exist is lower than the height position on the insertion side of the heat transfer tube 32. Has been extended.
  • the extending direction of the groove portion 35 provided on the surface of the fin 31 is defined as the ventilation direction K of the air flowing between the fins 31 in the z direction. Tilts in the opposite downward direction. Thereby, it becomes possible to further promote the drainage in the first region Pa where the drainage is easy, and the drainage can be carried out much more rapidly than in the first embodiment described above.
  • 1 refrigeration cycle device 2 compressor, 3 four-way valve, 4 indoor heat exchanger, 5 indoor fan, 6 expansion device, 7 outdoor fan, 10 indoor heat exchanger, 10A windward heat exchanger, 10B leeward heat exchanger 10C leeward header collecting pipe, 10D leeward header collecting pipe, 10E inter-row connecting member, 11, 21, 31, 101, 111, 210 fins, 12, 22, 32, 102, 112, 220 heat transfer pipes, 13, 20, 30, 100, 110, 200 heat exchanger, 14, 24, 34, 104, 114, 240 insertion hole, 14a, 24a, 34a, 240a, 240b end, 15, 15A, 25, 35, 35A, 35B , 250 groove part, 26 cut and raised part, 27 protruding part, H water drop, K air ventilation direction, P, Pa, T first area, Q, U second area , R, V third region.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention comprend : une pluralité d'ailettes en forme de plaque disposées de façon à être agencées côte à côte dans les directions avant et arrière à intervalles prédéfinis ; et une pluralité de tubes de transfert de chaleur comportant des sections transversales plates et disposés de façon à être agencés côte à côte dans la direction du côté long des ailettes à intervalles prédéfinis par rapport aux ailettes. Les tubes de transfert de chaleur ont été soumis à un traitement de surface, afin de retenir le caractère hydrophile sur leurs surfaces périphériques externes. Les ailettes comportent des sections de rainure s'étendant dans la direction du côté long et constituées de formes inégales agencées de façon à être adjacentes dans la direction du côté court orthogonale à la direction du côté long, et les ailettes ont été soumises à un traitement de surface, afin de retenir le caractère hydrophile. Ceci permet d'améliorer l'efficacité d'échange de chaleur, assurant en même temps des caractéristiques d'évacuation, même si les tubes de transfert de chaleur prennent des formes plates.
PCT/JP2018/039965 2018-10-26 2018-10-26 Échangeur de chaleur et dispositif à cycle frigorifique faisant appel audit échangeur WO2020084786A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2020552495A JP7112053B2 (ja) 2018-10-26 2018-10-26 熱交換器及びそれを用いた冷凍サイクル装置
CN201890000662.0U CN211290633U (zh) 2018-10-26 2018-10-26 热交换器以及使用该热交换器的制冷循环装置
PCT/JP2018/039965 WO2020084786A1 (fr) 2018-10-26 2018-10-26 Échangeur de chaleur et dispositif à cycle frigorifique faisant appel audit échangeur

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023100859A1 (fr) * 2021-12-02 2023-06-08 東芝キヤリア株式会社 Échangeur de chaleur
US11988462B2 (en) 2020-08-31 2024-05-21 Samsung Electronics Co., Ltd. Heat exchanger and air conditioner using the heat exchanger

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11108576A (ja) * 1997-10-02 1999-04-23 Nippon Light Metal Co Ltd 熱交換器
JP2012233680A (ja) * 2011-04-22 2012-11-29 Mitsubishi Electric Corp フィンチューブ型熱交換器及び冷凍サイクル装置
JP2013120044A (ja) * 2011-12-09 2013-06-17 Panasonic Corp フィンチューブ熱交換器とその製造方法
JP2013200119A (ja) * 2013-07-02 2013-10-03 Mitsubishi Electric Corp フィンチューブ熱交換器及びそれを用いた冷凍サイクル装置
WO2017017789A1 (fr) * 2015-07-28 2017-02-02 三菱電機株式会社 Échangeur de chaleur et appareil à cycle frigorifique

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4958184B2 (ja) 2007-01-25 2012-06-20 国立大学法人 東京大学 熱交換器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11108576A (ja) * 1997-10-02 1999-04-23 Nippon Light Metal Co Ltd 熱交換器
JP2012233680A (ja) * 2011-04-22 2012-11-29 Mitsubishi Electric Corp フィンチューブ型熱交換器及び冷凍サイクル装置
JP2013120044A (ja) * 2011-12-09 2013-06-17 Panasonic Corp フィンチューブ熱交換器とその製造方法
JP2013200119A (ja) * 2013-07-02 2013-10-03 Mitsubishi Electric Corp フィンチューブ熱交換器及びそれを用いた冷凍サイクル装置
WO2017017789A1 (fr) * 2015-07-28 2017-02-02 三菱電機株式会社 Échangeur de chaleur et appareil à cycle frigorifique

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11988462B2 (en) 2020-08-31 2024-05-21 Samsung Electronics Co., Ltd. Heat exchanger and air conditioner using the heat exchanger
WO2023100859A1 (fr) * 2021-12-02 2023-06-08 東芝キヤリア株式会社 Échangeur de chaleur

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JPWO2020084786A1 (ja) 2021-06-03
CN211290633U (zh) 2020-08-18

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