WO2019176061A1 - Échangeur de chaleur et dispositif à cycle de réfrigération - Google Patents

Échangeur de chaleur et dispositif à cycle de réfrigération Download PDF

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Publication number
WO2019176061A1
WO2019176061A1 PCT/JP2018/010282 JP2018010282W WO2019176061A1 WO 2019176061 A1 WO2019176061 A1 WO 2019176061A1 JP 2018010282 W JP2018010282 W JP 2018010282W WO 2019176061 A1 WO2019176061 A1 WO 2019176061A1
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Prior art keywords
heat exchanger
maximum
convex portion
air
windward
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PCT/JP2018/010282
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English (en)
Japanese (ja)
Inventor
暁 八柳
前田　剛志
石橋　晃
中村　伸
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.)
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2020506061A priority Critical patent/JP7313334B2/ja
Priority to PCT/JP2018/010282 priority patent/WO2019176061A1/fr
Publication of WO2019176061A1 publication Critical patent/WO2019176061A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • 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 that maintains heat transfer coefficient and reduces ventilation resistance, and a refrigeration cycle apparatus including the heat exchanger.
  • a conventional heat exchanger includes a plurality of heat transfer tubes arranged parallel to each other at intervals, and a plurality of fins connected to the plurality of heat transfer tubes and having surfaces parallel to the air flow direction. .
  • the air supplied to the heat exchanger passes between the plurality of heat transfer tubes and between the plurality of fins, and comes into contact with the heat transfer tubes and the fins. Thereby, heat exchange is performed between the heat exchange fluid that circulates in the heat transfer tube and the air that is the heat exchange fluid that exchanges heat with the heat exchange fluid.
  • a heat exchanger in which a plurality of cut-and-raised parts called slits or louvers that open in the direction of air flow is formed on the fin surface is also known.
  • a heat exchanger is called a slit fin heat exchanger.
  • the temperature boundary layer is reconstructed at each cut-and-raised part, and the air velocity near the fin surface increases. Thereby, since the amount of heat transport increases, the heat transfer rate of the heat exchanger is improved.
  • the cut-and-raised part may impede the discharge of condensed water, and a part of the air path in the heat exchanger may be blocked.
  • condensed water is the water which the water
  • a heat exchanger is also known in which corrugated irregularities protruding perpendicularly to the air flow direction are formed on the surface of the fin (see, for example, Patent Document 1).
  • a heat exchanger is called a slitless fin heat exchanger.
  • a secondary flow of air is generated due to an air current collision with a convex portion on the fin surface.
  • the heat transfer coefficient of the heat exchanger is improved.
  • the slitless fin heat exchanger has no cut-and-raised portion in the fin, the drainage of the condensed water is good, and frost formation is also prevented from being concentrated on a part of the fin. . Therefore, the slitless fin heat exchanger can ensure heat exchange performance under wet conditions.
  • the draft resistance increases due to the generation of the secondary flow and overcoming the convex portion of the secondary flow. For this reason, when the conventional slitless fin heat exchanger is applied to a refrigeration cycle apparatus, the blowing efficiency of the blower may be reduced, and the efficiency of the entire refrigeration cycle apparatus may be reduced.
  • the ventilation resistance it is conceivable to reduce the amplitude, wavelength, or angle of attack of the air flow with respect to the main flow of the corrugated irregularities formed on the fin.
  • the conventional heat exchanger had the subject that maintenance of a heat transfer rate and reduction of ventilation resistance were not able to be made compatible.
  • the present invention has been made to solve the above-described problems, and a first object thereof is to provide a heat exchanger that can reduce the ventilation resistance while maintaining the heat transfer coefficient. Moreover, this invention makes it the 2nd objective to provide the refrigerating-cycle apparatus provided with this heat exchanger.
  • the heat exchanger according to the present invention is a heat exchanger to which air is supplied by a blower, the heat transfer tube extending in a first direction which is a direction intersecting a flow direction of air supplied from the blower, and the heat transfer tube.
  • a second convex portion that is continuously formed along a direction intersecting with the air flow direction and is disposed on the downstream side of the first convex portion in the air flow direction, and
  • the first convex portion has a first maximum apex where the protruding height is maximum at the first convex portion
  • the second convex portion is a second maximum where the protruding height is maximum at the second convex portion.
  • the first maximum top and the second maximum top are in the direction of air flow. They are arranged at different positions in the orthogonal direction.
  • the refrigeration cycle apparatus includes the heat exchanger according to the present invention and a blower that supplies the air to the heat exchanger in the air flow direction.
  • the heat exchanger according to the present invention is a slitless fin heat exchanger.
  • the heat exchanger which concerns on this invention the possibility that the secondary flow over the 1st largest peak will get over the 2nd largest peak is reduced.
  • the heat exchanger which concerns on this invention can reduce the ventilation resistance at the time of a secondary flow getting over the convex part formed in the fin. Therefore, the heat exchanger according to the present invention can reduce the ventilation resistance while maintaining the heat transfer coefficient.
  • FIG. 4 is a sectional view taken along line AA in FIG. 3.
  • FIG. 4 is a sectional view taken along line BB in FIG.
  • FIG. 1 is a refrigerant circuit diagram illustrating an example of a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • a refrigeration cycle apparatus 1 according to Embodiment 1 will be described with reference to FIG.
  • the refrigeration cycle apparatus 1 is mounted on, for example, an air conditioner.
  • the heat exchange fluid flowing in the heat transfer tube of the heat exchanger of the refrigeration cycle apparatus 1 is a refrigerant
  • the heat exchange fluid that exchanges heat with the heat exchange fluid is air.
  • the flow of the refrigerant when the refrigeration cycle apparatus 1 performs the cooling operation is indicated by broken line arrows.
  • coolant in case the refrigeration cycle apparatus 1 performs heating operation is shown by the solid line arrow.
  • the refrigeration cycle apparatus 1 includes a compressor 2, an indoor heat exchanger 3, an indoor blower 4, an expansion device 5, an outdoor heat exchanger 6, an outdoor blower 7, and a four-way valve 8.
  • the compressor 2, the indoor heat exchanger 3, the expansion device 5, the outdoor heat exchanger 6, and the four-way valve 8 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 from the compressor 2 and sent to the four-way valve 8.
  • the compressor 2 can be composed of, for example, a rotary compressor, a scroll compressor, a screw compressor, or a reciprocating compressor.
  • the indoor heat exchanger 3 functions as a condenser during heating operation and functions as an evaporator during cooling operation.
  • the indoor heat exchanger 3 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 pipe heat exchanger, or a plate heat exchanger. Or the like.
  • An indoor fan 4 is provided in the vicinity of the indoor heat exchanger 3. The indoor blower 4 supplies the indoor heat exchanger 3 with air that is a heat exchange fluid.
  • the expansion device 5 expands and depressurizes the refrigerant that has flowed out of the indoor heat exchanger 3 or the outdoor heat exchanger 6.
  • the expansion device 5 may be constituted by, for example, an electric expansion valve that can adjust the flow rate of the refrigerant.
  • a mechanical expansion valve or a capillary tube that employs a diaphragm for the pressure receiving portion can be applied.
  • the outdoor heat exchanger 6 functions as an evaporator during heating operation and functions as a condenser during cooling operation.
  • An outdoor fan 7 is provided in the vicinity of the outdoor heat exchanger 6.
  • the outdoor blower 7 supplies the outdoor heat exchanger 6 with air that is a heat exchange fluid. The details of the outdoor heat exchanger 6 will be described later.
  • the four-way valve 8 switches the refrigerant flow between the heating operation and the cooling operation. That is, when the refrigeration cycle apparatus 1 performs the heating operation, the four-way valve 8 connects the discharge port of the compressor 2 and the indoor heat exchanger 3, and connects the suction port of the compressor 2 and the outdoor heat exchanger 6. Connecting. When the refrigeration cycle apparatus 1 performs the cooling operation, the four-way valve 8 connects the discharge port of the compressor 2 and the outdoor heat exchanger 6, and connects the suction port of the compressor 2 and the indoor heat exchanger 3. Connecting.
  • the high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 6 expands in the expansion device 5 and becomes a two-phase refrigerant in which a low-pressure gas refrigerant and a low-pressure liquid refrigerant are mixed.
  • the two-phase refrigerant flows into the indoor heat exchanger 3 that functions as an evaporator.
  • heat exchange is performed between the refrigerant in the two-phase state that has flowed in and the air supplied by the indoor blower 4.
  • the liquid refrigerant in the two-phase refrigerant evaporates and becomes a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant that has flowed out of the indoor heat exchanger 3 flows into the compressor 2 through the four-way valve 8, is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 2 again. Thereafter, this cycle is repeated.
  • the refrigeration cycle apparatus 1 performs the heating operation.
  • the compressor 2 When the compressor 2 is driven, high-temperature and high-pressure gaseous refrigerant is discharged from the compressor 2.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 2 flows into the indoor heat exchanger 3 functioning as a condenser via the four-way valve 8.
  • the indoor heat exchanger 3 heat exchange is performed between the flowing high-temperature and high-pressure gas refrigerant and the air supplied by the indoor blower 4.
  • the high-temperature and high-pressure gas refrigerant is condensed into a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant that has flowed out of the indoor heat exchanger 3 expands in the expansion device 5 and becomes a two-phase refrigerant in which a low-pressure gas refrigerant and a low-pressure liquid refrigerant are mixed.
  • the two-phase refrigerant flows into the outdoor heat exchanger 6 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 blower 7.
  • the liquid refrigerant in the two-phase refrigerant evaporates and becomes a low-pressure gas refrigerant.
  • the low-pressure gas refrigerant that has flowed out of the outdoor heat exchanger 6 flows into the compressor 2 via the four-way valve 8, is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 2 again. Thereafter, this cycle is repeated.
  • the refrigerant flowing out of the evaporator is a single-phase gas refrigerant.
  • the condensed water adhering to the outdoor heat exchanger 6 functioning as an evaporator may freeze and become frost or ice.
  • some refrigeration cycle apparatuses capable of heating operation execute a defrosting operation for removing frost attached to the outdoor heat exchanger 6 when the outside air becomes a certain temperature or lower.
  • the constant temperature is, for example, 0 degrees.
  • the defrosting operation is to supply a high-temperature and high-pressure gas refrigerant from the compressor 2 to the outdoor heat exchanger 6 in order to suppress frost from adhering to the outdoor heat exchanger 6 that functions as an evaporator.
  • the frost and ice adhering to the outdoor heat exchanger 6 are melted by the high-temperature and high-pressure gas refrigerant supplied to the outdoor heat exchanger 6.
  • the defrosting operation may be executed when the duration time of the heating operation reaches a predetermined time.
  • the predetermined time is, for example, 30 minutes.
  • the outdoor heat exchanger 6 is below a fixed temperature, it is good also as what performs a defrost operation before heating operation.
  • the constant temperature is, for example, minus 6 degrees.
  • a bypass refrigerant pipe is provided between the discharge port of the compressor 2 and the outdoor heat exchanger 6 so that the high-temperature and high-pressure gas refrigerant can be directly supplied from the compressor 2 to the outdoor heat exchanger 6 during the defrosting operation.
  • a four-way valve 8 can be used as the refrigerant flow switching device.
  • FIG. 2 is a perspective view showing an example of an outdoor heat exchanger in the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • the outdoor heat exchanger 6 is a fin-and-tube heat exchanger.
  • the outdoor heat exchanger 6 has, for example, a two-row structure, and includes an upwind heat exchanger 9 and a leeward heat exchanger 10.
  • the windward side heat exchanger 9 and the leeward side heat exchanger 10 are arranged in parallel along the X direction.
  • the X direction corresponds to the flow direction of the air supplied from the outdoor fan 7 to the outdoor heat exchanger 6.
  • the windward side heat exchanger 9 is arranged on the windward side, that is, upstream side of the leeward side heat exchanger 10 in the X direction.
  • the leeward heat exchanger 10 is arranged on the leeward side, that is, on the downstream side of the upwind heat exchanger 9 in the X direction.
  • the outdoor heat exchanger 6 includes a windward header collecting pipe 11, a leeward header collecting pipe 12, and an inter-row connecting member 13. Inside the leeward header collecting pipe 11, the leeward header collecting pipe 12, and the inter-row connecting member 13, a refrigerant as a working fluid flows.
  • the windward header collecting pipe 11 and the leeward header collecting pipe 12 are arranged in parallel along the X direction.
  • the windward header collecting pipe 11 has a refrigerant inlet / outlet port 11a.
  • the leeward header collecting pipe 12 has a refrigerant inlet / outlet 12a.
  • a heat transfer tube 14, which will be described later, provided in the windward heat exchanger 9 has one end connected to the windward header collecting tube 11 and the other end connected to the inter-row connecting member 13.
  • One end of the heat transfer tube provided in the leeward heat exchanger 10 is connected to the leeward header collecting tube 12, and the other end is connected to the inter-row connection member 13.
  • the windward side heat exchanger 9 and the leeward side heat exchanger 10 have the same configuration. For this reason, below, the wind-side heat exchanger 9 is demonstrated on behalf of both.
  • the outdoor heat exchanger 6 may be configured by only one of the windward side heat exchanger 9 or the leeward side heat exchanger 10. Good.
  • the upwind heat exchanger 9 corresponds to the heat exchanger in the present invention.
  • the windward side heat exchanger 9 includes a plurality of heat transfer tubes 14 and a plurality of fins 15.
  • the plurality of heat transfer tubes 14 are arranged so as to extend along the Y direction orthogonal to the X direction.
  • the Y direction is the horizontal direction.
  • a refrigerant circulates inside the heat transfer tube 14.
  • the plurality of heat transfer tubes 14 are arranged in parallel and spaced apart from each other in the Z direction orthogonal to the X direction and the Y direction.
  • the Z direction is the vertical direction.
  • the plurality of heat transfer tubes 14 are made of, for example, an aluminum alloy.
  • the Y direction corresponds to the first direction in the present invention.
  • the plurality of fins 15 are elongated plate-like members having a surface 15a parallel to the X direction.
  • the plurality of fins 15 are plate fins, for example. That is, the windward side heat exchanger 9 is a plate fin and tube type heat exchanger.
  • the plurality of fins 15 are arranged so as to extend along the Z direction in which the heat transfer tubes 14 are arranged. Further, the plurality of fins 15 are arranged at intervals in the Y direction in which the heat transfer tube 14 extends.
  • the plurality of fins 15 are made of, for example, an aluminum alloy.
  • a plurality of heat transfer tubes 14 penetrates the surfaces 15a of the plurality of fins 15.
  • the air supplied to the upwind heat exchanger 9 by the outdoor blower 7 passes between the plurality of heat transfer tubes 14 and between the plurality of fins 15 in contact with the plurality of heat transfer tubes 14 and the plurality of fins 15.
  • the refrigerant that has flowed into the windward header collecting pipe 11 from the refrigerant inlet / outlet 11 a is distributed to the plurality of heat transfer tubes 14 of the windward heat exchanger 9.
  • the refrigerant flowing through the plurality of heat transfer tubes 14 flows into the inter-row connecting member 13.
  • the refrigerant that has flowed into the inter-row connecting member 13 is distributed to the plurality of heat transfer tubes of the leeward heat exchanger 10.
  • the refrigerant that has flowed through the plurality of heat transfer tubes of the leeward heat exchanger 10 joins at the leeward header collecting pipe 12 and flows out from the refrigerant inlet / outlet 12a.
  • coolant is not limited to this, A reverse direction may be sufficient.
  • the upwind heat exchanger 9 shown in FIG. 2 is a side flow type heat exchanger in which the Y direction is the horizontal direction and the Z direction is the vertical direction.
  • the windward side heat exchanger 9 is not limited to a side flow type heat exchanger.
  • the upwind heat exchanger 9 may be a downflow type heat exchanger in which the Y direction is the vertical direction and the Z direction is the horizontal direction.
  • the X direction, the Y direction, and the Z direction need not be parallel to each other, and are not limited to the above-described directions. In other words, the X direction, the Y direction, and the Z direction only need to intersect each other, and do not have to be arranged at right angles.
  • the air supplied to the outdoor heat exchanger 6 by the outdoor blower 7 sequentially passes through the windward side heat exchanger 9 and the leeward side heat exchanger 10.
  • the air supplied to the windward side heat exchanger 9 passes between the plurality of heat transfer tubes 14 and between the plurality of fins 15 while being in contact with the plurality of heat transfer tubes 14 and the plurality of fins 15. Since the heat transfer tubes 14 and the fins 15 are connected, the heat of the refrigerant flowing through the heat transfer tubes 14 is transmitted to the heat transfer tubes 14 and the fins 15. That is, the surfaces of the plurality of heat transfer tubes 14 and the plurality of fins 15 are heat transfer surfaces. Heat exchange is performed between these heat transfer surfaces and the air passing through the windward heat exchanger 9.
  • the heat exchange in the leeward heat exchanger 10 is also the same as that of the leeward heat exchanger 9.
  • FIG. 3 is a cross-sectional view showing a main part of the upside heat exchanger of the outdoor heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 3 is a cross-sectional view of the main part of the windward heat exchanger 9 observed in a direction parallel to the Y direction and opposite to the Y direction.
  • FIG. 3 shows two heat transfer tubes 14 as a representative.
  • the solid line drawn on the surface of the fin 15 indicates a portion protruding toward the front side of the drawing.
  • the broken line drawn on the surface of the fin 15 in FIG. 3 indicates a portion recessed on the back side of the drawing.
  • the direction parallel to the Y direction and opposite to the Y direction corresponds to the second direction of the present invention.
  • a direction parallel to the Y direction and opposite to the Y direction is referred to as a minus Y direction.
  • the cross section of the heat transfer tube 14 has a circular shape.
  • a flow path 14 a through which the refrigerant flows is formed along the Y direction.
  • the flow path 14a has a circular shape.
  • the heat transfer tubes 14 and the fins 15 are brought into close contact with each other by mechanically expanding the heat transfer tubes 14.
  • the heat transfer tubes 14 and the fins 15 may be brought into close contact with each other by brazing.
  • the cross-sectional shape of the heat transfer tube 14 is not limited to a circular shape, and may be an elliptical shape or a flat shape.
  • the shape of the flow path 14a is not limited to a circular shape, and may be an elliptical shape or a rectangular shape.
  • the number of the flow paths 14a formed in one heat transfer tube 14 is not limited to one, and may be plural.
  • a plurality of convex portions 16 are formed on the surface 15 a of the fin 15.
  • One convex part 16 becomes the range between adjacent broken lines. That is, the plurality of convex portions 16 protrude in the Y direction. Moreover, the some convex part 16 is continuously formed along the Z direction, respectively. In other words, the plurality of convex portions 16 are continuously formed along the direction intersecting the X direction.
  • Each ridgeline R of the plurality of convex portions 16 is, for example, a straight line parallel to the Z direction.
  • the fin 15 becomes a wave side shape seeing from a Z direction by the several convex part 16 being arrange
  • Each of the plurality of convex portions 16 has a maximum apex portion 16a indicated by a black dot in FIG.
  • the maximum apex portion 16a is a portion where the protrusion height in the Y direction is maximum in the same convex portion 16.
  • FIG. 3 shows an example in which each of the plurality of convex portions 16 has a plurality of maximum apex portions 16a. That is, each of the plurality of convex portions 16 has a wave shape when viewed from the X direction. Note that the number of the maximum apex portions 16a in each of the plurality of convex portions 16 is not limited to a plurality, and may be one.
  • the plurality of convex portions 16 includes a first convex portion 17 and a second convex portion 18 formed on the downstream side in the X direction from the first convex portion 17.
  • one of the plurality of convex portions 16 is the first convex portion 17.
  • one of the convex portions 16 formed on the downstream side in the X direction from the first convex portion 17 is the second convex portion 18.
  • the 1st convex part 17 has the 1st largest peak part 17a from which the protrusion height to the Y direction becomes the maximum in the 1st convex part 17.
  • the 2nd convex part 18 has the 2nd largest peak part 18a from which the protrusion height to the Y direction becomes the maximum in the 2nd convex part 18.
  • FIG. The first maximum apex portion 17a and the second maximum apex portion 18a are arranged at different positions in the Z direction. In other words, the first maximum apex portion 17a and the second maximum apex portion 18a are arranged at different positions in the direction orthogonal to the flow direction of the air supplied from the outdoor blower 7. That is, the first maximum apex portion 17a and the second maximum apex portion 18a are not arranged on the same line in the X direction.
  • the 1st convex part 17 is exhibiting the waveform shape seeing from the X direction.
  • the second convex portion 18 also has a wave shape when viewed from the X direction.
  • the 1st convex part 17 has the slope part 17b inclined with respect to the Y direction.
  • the second convex portion 18 also has a slope portion 18 b that is inclined with respect to the Y direction.
  • the first maximum apex portion 17a and the second maximum apex portion 18a have the same protruding height in the Y direction.
  • FIG. 5 is a cross-sectional view taken along the line BB in FIG. As shown in FIG. 5, the slope part 17b of the 1st convex part 17 is arrange
  • a part of the air supplied to the fins 15 collides with the slope part 17b of the first convex part 17 to generate a secondary flow.
  • a part of the secondary flow generated by colliding with the slope portion 17b rises along the slope portion 17b and gets over the first maximum apex portion 17a.
  • Part of the air that has passed over the first maximum apex portion 17a flows in the X direction while maintaining the altitude as it is.
  • the air that has passed over the first maximum apex portion 17a does not collide with the second convex portion 18. Flows downstream in the X direction.
  • the heat transfer performance, frosting resistance, and drainage action of the upwind heat exchanger 9 will be described.
  • the frosting resistance indicates the difficulty of blocking the air passage in the heat exchanger when the heat exchanger is frosted.
  • the configurations of the heat exchangers of Comparative Example 1, Comparative Example 2, and Comparative Example 3 will be described.
  • heat transfer performance, frosting resistance, and drainage action of the heat exchangers of Comparative Example 1, Comparative Example 2, and Comparative Example 3 will be described.
  • the heat transfer performance, frost proof strength, and drainage action of the windward side heat exchanger 9 according to Embodiment 1 will be described.
  • Comparative Example 1 When showing Comparative Example 1 to Comparative Example 3, “1000”, “2000”, and “3000” are added to the configuration of the comparative example in the configuration of the first embodiment corresponding to the configuration.
  • a reference sign shall be attached.
  • the windward heat exchanger of Comparative Example 1 is the windward heat exchanger 1009
  • the windward heat exchanger of Comparative Example 2 is the windward heat exchanger 2009
  • the windward heat exchanger of Comparative Example 3 is the windward heat exchanger.
  • FIG. 6 is a cross-sectional view illustrating a main part of the windward heat exchanger according to Comparative Example 1.
  • FIG. 6 is a view of the windward side heat exchanger 1009 according to the comparative example 1 in the same observation direction and observation range as those in FIG.
  • two heat transfer tubes 1014 are shown as a representative of the plurality of heat transfer tubes 1014.
  • FIG. 6 also shows the flow path 1014a of these heat transfer tubes 1014.
  • the upwind heat exchanger 1009 of Comparative Example 1 is different from the upwind heat exchanger 9 in that the fin 1015 does not include the plurality of convex portions 16.
  • the surface 1015a of the fin 1015 is formed in a planar shape.
  • the surface 1015a of the upwind heat exchanger 1009 of Comparative Example 1 is formed in a flat shape. For this reason, the upwind heat exchanger 1009 of the comparative example 1 is excellent in the drainage performance of condensed water. Moreover, the windward side heat exchanger 1009 of the comparative example 1 is excellent in frosting yield strength. On the other hand, since the secondary flow generated on the surface 1015a is small, the flow velocity of the air flowing near the surface of the surface 1015a cannot be increased. That is, in the windward side heat exchanger 1009 of Comparative Example 1, sufficient heat transfer performance cannot be obtained.
  • FIG. 7 is a cross-sectional view illustrating a main part of the upwind heat exchanger according to the second comparative example.
  • FIG. 7 is a view of the windward heat exchanger 2009 according to the comparative example 2 in the same observation direction and observation range as those in FIG.
  • two heat transfer tubes 2014 are shown as a representative of the plurality of heat transfer tubes 2014.
  • FIG. 7 also shows the flow paths 2014a of these heat transfer tubes 2014.
  • the upwind heat exchanger 2009 of the comparative example 2 is demonstrated.
  • the upwind heat exchanger 2009 of the comparative example 2 is different from the upwind heat exchanger 9 in that a cut-and-raised portion 2019 is formed on the fin 2015. That is, the windward side heat exchanger 2009 is a slit fin heat exchanger.
  • the temperature boundary layer is reconstructed in the cut-and-raised part 2019, and the flow velocity of the air flowing in the vicinity of the surface 2015a increases.
  • the windward side heat exchanger 2009 is excellent in heat transfer performance.
  • the ventilation resistance is increased by the cut-and-raised portion 2019.
  • condensed water is cut and raised and held in 2019, drainage performance is not sufficient.
  • frost formation is concentrated on the cut-and-raised portion 2019.
  • frost blocks a part of the air path in the windward side heat exchanger 2009. That is, while the upwind heat exchanger 2009 of Comparative Example 2 may improve the refrigeration cycle efficiency, sufficient drainage performance and frosting resistance cannot be obtained.
  • FIG. 8 is a cross-sectional view illustrating a main part of the upwind heat exchanger according to Comparative Example 3.
  • FIG. 8 is a view of the windward side heat exchanger 3009 according to Comparative Example 3 in the same observation direction and observation range as in FIG.
  • two heat transfer tubes 3014 are shown as a representative of the plurality of heat transfer tubes 3014.
  • FIG. 8 also shows a flow path 3014a of these heat transfer tubes 3014.
  • a solid line drawn on the surface of the fin 3015 indicates a portion protruding toward the front side of the drawing.
  • a broken line drawn on the surface of the fin 3015 in FIG. 8 indicates a portion recessed on the back side of the drawing.
  • FIG. 9 is a cross-sectional view taken along the line CC in FIG.
  • the configuration of the upwind heat exchanger 3009 of Comparative Example 3 will be described with reference to FIGS.
  • the upwind heat exchanger 3009 of Comparative Example 3 is different from the upwind heat exchanger 9 in that the first maximum apex 3017a of the first convex portion 3017 and the second maximum apex 3018a of the second convex portion 3018 are in the Z direction. It is a point which is not arrange
  • the upwind heat exchanger 3009 of Comparative Example 3 has a plurality of convex portions 3016 having a wave shape on the surface 3015a. For this reason, the air which collided with the some convex part 3016 produces
  • the upwind heat exchanger 3009 of the comparative example 3 can prevent the condensed water from being held by the cut-and-raised portion 2019, and can also prevent frost formation from being concentrated on the cut-and-raised portion 2019. Thereby, the upwind heat exchanger 3009 of the comparative example 3 can obtain sufficient drainage performance and frosting resistance.
  • the first maximum apex 3017a and the second maximum apex 3018a are arranged on the same line in the X direction. For this reason, there is a high possibility that the air that has passed over the first maximum apex 3017a will get over the second maximum apex 3018a, and the ventilation resistance will increase. That is, the windward side heat exchanger 3009 of Comparative Example 3 can obtain sufficient drainage performance and frosting resistance, while the refrigeration cycle efficiency may decrease due to an increase in ventilation resistance.
  • the windward heat exchanger 9 according to the first embodiment includes a plurality of convex portions 16 as in the comparative example 3. Therefore, the air colliding with the plurality of convex portions 16 generates a secondary flow, and the flow velocity of the air flowing in the vicinity of the surface 15a increases. Thereby, since the amount of heat transport increases, the windward heat exchanger 9 is excellent in heat transfer performance. Further, the fin 15 does not have the cut-and-raised portion 2019. For this reason, the upwind heat exchanger 9 according to the first embodiment can prevent the condensed water from being held by the cut-and-raised portion 2019, and can prevent frost from being concentrated on the cut-and-raised portion 2019. it can. Thereby, the upwind heat exchanger 9 according to the first embodiment can obtain sufficient drainage performance and frost resistance.
  • the first maximum apex portion 17a and the second maximum apex portion 18a are arranged at different positions in the Z direction. That is, the first maximum peak portion 17a and the second maximum peak portion 18a are not arranged on the same line in the X direction. For this reason, possibility that the air which got over the 1st largest peak part 17a will get over the 2nd largest peak part 18a is reduced. Thereby, the ventilation resistance produced when air gets over the some convex part 16 is reduced. That is, the windward side heat exchanger 9 can improve the refrigeration cycle efficiency without impairing the drainage performance and the frosting resistance. Further, by improving the efficiency of the refrigeration cycle, the upwind heat exchanger 9 can be made compact and the cost can be reduced.
  • the upwind heat exchanger 9 is a heat exchanger to which air is supplied by the outdoor blower 7.
  • the windward side heat exchanger 9 includes a heat transfer tube 14 extending in the Y direction that intersects the X direction that is a flow direction of the air supplied from the outdoor blower 7, and fins 15 that are connected to the heat transfer tube 14. I have.
  • the fin 15 has the 1st convex part 17 which protruded in the Y direction and was continuously formed along the direction which cross
  • the fin 15 has a second convex portion 18 that protrudes in the Y direction and is continuously formed along the direction intersecting the X direction, and is disposed on the downstream side of the first convex portion 17 in the X direction.
  • the first convex portion 17 has a first maximum apex portion 17a at which the protruding height at the first convex portion 17 is maximum.
  • the 2nd convex part 18 has the 2nd largest peak part 18a from which the protrusion height becomes the maximum in this 2nd convex part 18. As shown in FIG.
  • the first maximum apex portion 17a and the second maximum apex portion 18a are arranged at different positions in the direction orthogonal to the X direction.
  • the windward side heat exchanger 9 according to Embodiment 1 is a slitless fin heat exchanger. Further, in the windward heat exchanger 9 according to the first embodiment, the possibility that the secondary flow over the first maximum top portion 17a gets over the second maximum top portion 18a is reduced. For this reason, the windward side heat exchanger 9 according to the first embodiment can reduce the ventilation resistance when the secondary flow gets over the convex portions 16 formed on the fins 15. Therefore, the upwind heat exchanger 9 according to the first embodiment can reduce the ventilation resistance while maintaining the heat transfer coefficient.
  • the plurality of fins 15 may be corrugated fins in which flat portions and curved surface portions are alternately arranged by bending a plate-like member. That is, the windward side heat exchanger 9 may be a corrugated fin and tube heat exchanger. Further, the windward heat exchanger 9 may be a microchannel heat exchanger.
  • the number of the plurality of convex portions 16 is not limited and may be two or more. By arranging the plurality of convex portions 16 in close contact with each other, a secondary flow is constantly generated, so that the flow velocity of the air flowing in the vicinity of the surface 15a increases. Thereby, since the amount of heat transport increases, the heat transfer performance is improved.
  • the apparatus on which the refrigeration cycle apparatus 1 is mounted is not limited to an air conditioner.
  • the refrigeration cycle apparatus 1 can be mounted on various apparatuses having a refrigeration cycle circuit such as a refrigerator. That is, the refrigeration cycle apparatus according to the present invention can be mounted on various apparatuses having a refrigeration cycle circuit.
  • FIG. 1 The shapes of the first convex portion 17 and the second convex portion 18 are not limited to the shapes shown in the first embodiment. If the first maximum apex portion 17a and the second maximum apex portion 18a are arranged at different positions in the direction orthogonal to the X direction, the first convex portion 17 and the second convex portion 18 can be formed in various shapes. . In the second embodiment, an example of the shape of the first convex portion 17 and the second convex portion 18 will be described. In the second embodiment, items not particularly described are the same as those in the first embodiment.
  • FIG. 10 is a cross-sectional view showing a main part of an example of an upwind heat exchanger according to Embodiment 2 of the present invention.
  • FIG. 10 is a view of an example of the windward side heat exchanger 9 according to the second embodiment in the same observation direction and observation range as those in FIG.
  • the solid line drawn on the surface of the fin 15 indicates a portion protruding toward the front side of the drawing.
  • the broken line drawn on the surface of the fin 15 in FIG. 10 has shown the location dented in the paper surface back side.
  • FIG. 11 is a perspective view showing a part of the fin surface of the windward heat exchanger shown in FIG. In FIG. 11, the ridgeline R of the convex portion 16 is indicated by a thick solid line.
  • a plurality of protrusions 21 are continuously formed on the fins 15 of the windward heat exchanger 9 shown in FIGS.
  • Each of the plurality of protrusions 21 has a quadrangular pyramid shape protruding in the Y direction.
  • the plurality of convex portions 16 can be continuously formed along the direction intersecting the X direction.
  • the some convex part 16 can be arrange
  • each of the plurality of convex portions 16 has a maximum apex portion 16a.
  • one of the plurality of convex portions 16 is defined as a first convex portion 17. Further, among the plurality of convex portions 16, one of the convex portions 16 formed on the downstream side in the X direction from the first convex portion 17 is referred to as a second convex portion 18.
  • the first convex portion 17 has a first maximum apex portion 17a at which the protrusion height in the Y direction is maximum in the first convex portion 17.
  • the second convex portion 18 has a second maximum apex portion 18a at which the protrusion height in the Y direction at the second convex portion 18 is maximum.
  • the first maximum apex portion 17a and the second maximum apex portion 18a are arranged at different positions in the Z direction.
  • the first maximum apex portion 17a and the second maximum apex portion 18a are arranged at different positions in the direction orthogonal to the flow direction of the air supplied from the outdoor blower 7. That is, the first maximum apex portion 17a and the second maximum apex portion 18a are not arranged on the same line in the X direction.
  • FIG. 12 is a cross-sectional view showing a main part of another example of the windward heat exchanger according to Embodiment 2 of the present invention.
  • This FIG. 12 is the figure which looked at another example of the upwind heat exchanger 9 which concerns on this Embodiment 2 in the observation direction and observation range similar to FIG.
  • the solid line drawn on the surface of the fin 15 indicates a portion protruding toward the front side of the paper.
  • the broken line drawn on the surface of the fin 15 in FIG. 12 has shown the location dented in the paper surface back side.
  • FIG. 13 is a perspective view showing a part of the fin surface of the windward heat exchanger shown in FIG. In FIG. 13, the ridgeline R of the convex portion 16 is indicated by a thick solid line.
  • a plurality of protrusions 22 are continuously formed on the fins 15 of the upwind heat exchanger 9 shown in FIGS.
  • each of the plurality of protrusions 22 is configured by three surfaces that are in contact with the same corner portion among surfaces forming a cube or a rectangular parallelepiped.
  • each of the some protrusion 22 is formed in the fin 15 so that the said same corner
  • the plurality of protrusions 22 can be continuously formed along the direction intersecting the X direction.
  • the some convex part 16 can be arrange
  • each of the plurality of convex portions 16 has a maximum apex portion 16a.
  • the ridgeline R of the convex part 16 is continuously formed in the zigzag shape along the direction which cross
  • the convex portions 16 are continuously formed in a zigzag shape along the direction intersecting the X direction.
  • one of the plurality of convex portions 16 is defined as a first convex portion 17.
  • the convex portion 16 formed on the downstream side in the X direction from the first convex portion 17 is referred to as a second convex portion 18.
  • the first convex portion 17 has a first maximum apex portion 17a at which the protrusion height in the Y direction is maximum in the first convex portion 17.
  • the second convex portion 18 has a second maximum apex portion 18a at which the protrusion height in the Y direction at the second convex portion 18 is maximum.
  • the first maximum apex portion 17a and the second maximum apex portion 18a are arranged at different positions in the Z direction.
  • the first maximum apex portion 17a and the second maximum apex portion 18a are arranged at different positions in the direction orthogonal to the flow direction of the air supplied from the outdoor blower 7. That is, the first maximum apex portion 17a and the second maximum apex portion 18a are not arranged on the same line in the X direction.
  • connection portion between the adjacent convex portions 16 is a concave portion.
  • the heat transfer performance of the windward heat exchanger 9 can be improved by projecting the concave portion, which is a connection point between the adjacent convex portions 16, in the minus Y direction.
  • the windward heat exchanger 9 which concerns on this Embodiment 3 is demonstrated by the example which deform
  • FIG. in the third embodiment items that are not particularly described are the same as those in the first or second embodiment.
  • FIG. 14 is a cross-sectional view showing a main part of an example of an upwind heat exchanger according to Embodiment 3 of the present invention.
  • FIG. 14 is a view of an example of the windward heat exchanger 9 according to the third embodiment in the same observation direction and observation range as those in FIG.
  • the solid line drawn on the surface of the fin 15 indicates a portion protruding toward the front side of the paper.
  • the broken line drawn on the surface of the fin 15 in FIG. 14 has shown the location dented in the paper surface back side.
  • FIG. 15 is a sectional view taken along the line DD in FIG.
  • FIG. 16 is a cross-sectional view taken along line EE in FIG.
  • a concave portion that is a connecting portion of the adjacent convex portions 16 protrudes in the minus Y direction.
  • a concave portion that is a connecting portion between adjacent convex portions 16 protrudes in the minus Y direction with respect to the surface 15 a of the fin 15.
  • the some convex part 26 is formed in the surface on the opposite side to the side from which the convex part 16 protrudes in the fin 15.
  • Each of the plurality of convex portions 26 is continuously formed along the Z direction. In other words, the plurality of convex portions 26 are continuously formed along the direction intersecting the X direction.
  • Each ridgeline R of the plurality of convex portions 26 is, for example, a straight line parallel to the Z direction.
  • the fin 15 of the windward heat exchanger 9 according to the third embodiment includes the third convex portion 27 that is one of the plurality of convex portions 26.
  • the fin 15 of the upwind heat exchanger 9 according to the third embodiment is one of the number of convex portions 26 and is formed on the downstream side in the X direction from the third convex portion 27.
  • a fourth convex portion 28 is provided.
  • the third convex portion 27 is disposed between the first convex portion 17 and the second convex portion 18.
  • the 4th convex part 28 is arranged in the downstream of the 2nd convex part 18 in the X direction.
  • the air that has collided with the plurality of convex portions 26 generates a secondary flow. That is, by configuring the fin 15 as in the third embodiment, a secondary flow can be generated even on the surface of the fin 15 opposite to the side on which the convex portion 16 protrudes. Therefore, by configuring the fins 15 as in the third embodiment, the heat transfer performance of the upwind heat exchanger 9 can be improved as compared with the first and second embodiments.
  • each of the plurality of convex portions 16 has a maximum apex portion 26a indicated by a black dot in FIG.
  • the maximum apex portion 26a is a portion where the protrusion height in the minus Y direction is maximum in the same convex portion 26.
  • FIG. 15 shows an example in which each of the plurality of convex portions 26 has a plurality of maximum apex portions 26a. That is, each of the plurality of convex portions 26 has a wave shape when viewed from the X direction. Note that the number of maximum apex portions 26a in each of the plurality of convex portions 26 is not limited to a plurality, and may be one.
  • the third convex portion 27 has a third maximum apex portion 27a at which the protrusion height in the minus Y direction is maximum at the third convex portion 27.
  • the fourth convex portion 28 has a fourth maximum apex portion 28a at which the protrusion height in the minus Y direction is maximum in the fourth convex portion 28.
  • the third maximum apex portion 27a and the fourth maximum apex portion 28a are arranged at different positions in the Z direction. In other words, the third maximum apex portion 27a and the fourth maximum apex portion 28a are arranged at different positions in the direction orthogonal to the flow direction of the air supplied from the outdoor blower 7. That is, the third maximum apex 27a and the fourth maximum apex 28a are not arranged on the same line in the X direction.
  • the windward heat exchanger 9 according to the third embodiment can also reduce the ventilation resistance when the secondary flow gets over the plurality of convex portions 26 formed on the fins 15.
  • Embodiment 4 By modifying the windward heat exchanger 9 according to the first to third embodiments as in the fourth embodiment, the frosting resistance of the windward heat exchanger 9 can be improved.
  • items not particularly described are the same as those in any of the first to third embodiments.
  • FIG. 17 is sectional drawing which shows the principal part of an example of the windward heat exchanger which concerns on Embodiment 4 of this invention.
  • FIG. 17 is a view of an example of the windward side heat exchanger 9 according to the fourth embodiment in the same observation direction and observation range as FIG.
  • the protruding height of the first maximum apex portion 17a of the first convex portion 17 is lower than the protruding height of the second maximum apex portion 18a of the second convex portion 18. It has become.
  • the local heat transfer coefficient around the first convex portion 17 that is on the windward side from the second convex portion 18 is lower than the first convex portion 17. It becomes smaller than the local heat transfer coefficient around the second convex portion 18.
  • the windward heat exchanger 9 functions as an evaporator
  • the air supplied from the outdoor blower 7 to the windward heat exchanger 9 is cooled by the windward heat exchanger 9. That is, when the windward heat exchanger 9 functions as an evaporator, the amount of absolute humidity of the air flowing through the windward heat exchanger 9 increases toward the windward side.
  • the windward side heat exchanger 9 functions as an evaporator, the windward side heat exchanger 9 is more likely to be frosted toward the windward side. Therefore, by configuring the first convex portion 17 and the second convex portion 18 as shown in FIG. 17, in the windward side heat exchanger 9, it is possible to reduce the local heat transfer coefficient on the windward side where frost formation is likely to occur. It is possible to suppress the air path in the windward side heat exchanger 9 from being blocked by frost formation. For this reason, by forming the 1st convex part 17 and the 2nd convex part 18 like FIG. 17, the frost proof stress of the windward heat exchanger 9 can be improved.
  • the third convex part 27 and the fourth convex part 28 are as follows. You may comprise as follows.
  • FIG. 18 is sectional drawing which shows the principal part of another example of the windward heat exchanger which concerns on Embodiment 4 of this invention.
  • This FIG. 18 is the figure which looked at another example of the windward heat exchanger 9 which concerns on this Embodiment 4 in the observation direction and observation range similar to FIG.
  • the protruding height of the third maximum apex 27 a of the third convex portion 27 is lower than the protruding height of the fourth maximum apex 28 a of the fourth convex portion 28. .
  • the local heat transfer coefficient around the third convex portion 27 that is on the windward side from the fourth convex portion 28 is lower than the third convex portion 27. It becomes smaller than the local heat transfer coefficient around the fourth convex portion 28. For this reason, by forming the 3rd convex part 27 and the 4th convex part 28 like FIG. 18, in the windward heat exchanger 9 which has the 3rd convex part 27 and the 4th convex part 28, it is easy to form frost. The local heat transfer coefficient on the windward side can be reduced.
  • the windward heat exchanger 9 having the third convex portion 27 and the fourth convex portion 28 it is possible to further suppress the air path in the windward heat exchanger 9 from being blocked by frost formation. For this reason, by forming the 3rd convex part 27 and the 4th convex part 28 like FIG. 18, the frost proof stress of the windward heat exchanger 9 which has the 3rd convex part 27 and the 4th convex part 28 is improved. Can be made.
  • Refrigeration cycle device 2 compressor, 3 indoor heat exchanger, 4 indoor blower, 5 throttle device, 6 outdoor heat exchanger, 7 outdoor blower, 8 four-way valve, 9 upwind heat exchanger (heat exchanger), 10 Leeward heat exchanger, 11 leeward header collecting pipe, 11a refrigerant inlet / outlet, 12 leeward header collecting pipe, 12a refrigerant inlet / outlet, 13 inter-row connecting member, 14 heat transfer pipe, 14a flow path, 15 fin, 15a surface, 16 convex Part, 16a maximum top, 17 first convex part, 17a first maximum top part, 17b slope part, 18 second convex part, 18a second maximum top part, 18b slope part, 21 projections, 22 projections, 26 convex parts, 26a maximum Top, 27 3rd convex part, 27a 3rd largest peak, 28 4th convex part, 28a 4th largest peak, 1009 Upwind heat exchanger, 1014 Heat transfer tube, 10 4a flow path, 1015 fin, 1015a face, 2009

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

Abstract

La présente invention concerne un échangeur de chaleur qui est configuré de sorte que de l'air soit distribué à celui-ci par une soufflante qui est pourvue de : un tuyau de transfert de chaleur s'étendant dans une première direction croisant une direction dans laquelle l'air fourni par la soufflante s'écoule ; et une ailette reliée au tuyau de transfert de chaleur. L'ailette comporte des premières saillies qui font saillie dans la première direction et qui sont formées de façon continue dans une direction croisant la direction dans laquelle l'air s'écoule ; et des deuxièmes saillies qui font saillie dans la première direction, sont formées de façon continue dans la direction croisant la direction dans laquelle l'air s'écoule, et sont disposées en aval des premières saillies dans la direction dans laquelle l'air s'écoule. Les premières saillies ont des premières sections supérieures les plus hautes où la hauteur de saillie des premières sailies est la plus élevée. Les deuxièmes saillies ont des deuxièmes sections supérieures les plus hautes où la hauteur de saillie des deuxièmes saillies est la plus élevée. Les premières sections supérieures les plus hautes et les deuxièmes sections supérieures les plus hautes sont agencées à des positions différentes dans une direction perpendiculaire à la direction dans laquelle l'air s'écoule.
PCT/JP2018/010282 2018-03-15 2018-03-15 Échangeur de chaleur et dispositif à cycle de réfrigération WO2019176061A1 (fr)

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PCT/JP2018/010282 WO2019176061A1 (fr) 2018-03-15 2018-03-15 Échangeur de chaleur et dispositif à cycle de réfrigération

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JP2001174181A (ja) * 1999-10-06 2001-06-29 Mitsubishi Heavy Ind Ltd フィンアンドチューブ熱交換器及びこれを備えた空気調和機
CN103925828A (zh) * 2014-04-03 2014-07-16 东华大学 一种具有球型凸起的散热翅片

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JPS6027916B2 (ja) * 1978-04-24 1985-07-02 ダイキン工業株式会社 熱交換器
US20090199585A1 (en) * 2006-03-23 2009-08-13 Matsushita Electric Industrial Co., Ltd. Fin-tube heat exchanger, fin for heat exchanger, and heat pump apparatus
DE102014107408B4 (de) * 2014-05-26 2022-07-14 Kelvion Machine Cooling Systems Gmbh Wärmetauscher

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JPS5086359U (fr) * 1973-12-11 1975-07-23
JPS63190778U (fr) * 1987-05-26 1988-12-08
JP2001174181A (ja) * 1999-10-06 2001-06-29 Mitsubishi Heavy Ind Ltd フィンアンドチューブ熱交換器及びこれを備えた空気調和機
CN103925828A (zh) * 2014-04-03 2014-07-16 东华大学 一种具有球型凸起的散热翅片

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KR102660705B1 (ko) * 2022-12-29 2024-04-26 고려대학교 산학협력단 열교환기

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