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WO2019180817A1 - Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation - Google Patents

Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation Download PDF

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Publication number
WO2019180817A1
WO2019180817A1 PCT/JP2018/011044 JP2018011044W WO2019180817A1 WO 2019180817 A1 WO2019180817 A1 WO 2019180817A1 JP 2018011044 W JP2018011044 W JP 2018011044W WO 2019180817 A1 WO2019180817 A1 WO 2019180817A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
groove
refrigerant
heat transfer
heat
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2018/011044
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English (en)
Japanese (ja)
Inventor
裕樹 宇賀神
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2018/011044 priority Critical patent/WO2019180817A1/fr
Priority to JP2020507166A priority patent/JP6925508B2/ja
Priority to CN201880091134.5A priority patent/CN111886459A/zh
Priority to EP18911206.3A priority patent/EP3770535A4/fr
Publication of WO2019180817A1 publication Critical patent/WO2019180817A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/06—Tubular elements of cross-section which is non-circular crimped or corrugated in cross-section
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • 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 performs heat exchange, a refrigeration cycle apparatus, and an air conditioner.
  • the present invention relates to a heat exchanger having a heat transfer tube provided with a groove on the inner surface of the tube.
  • a heat exchanger used in a refrigeration cycle apparatus such as a refrigeration apparatus, an air conditioner, or a heat pump
  • an inner surface is formed so as to penetrate through holes provided in each fin with respect to fins arranged in plural at a predetermined interval.
  • a heat transfer tube in which a groove is formed is disposed.
  • the heat transfer tube becomes a part of a refrigerant circuit in the refrigeration cycle apparatus, and a fluid such as a refrigerant flows inside.
  • the refrigerant is a fluid.
  • phase change condensation or evaporation
  • the refrigerant flowing through such a heat transfer tube undergoes phase change (condensation or evaporation) by heat exchange with air flowing outside the heat transfer tube.
  • phase change condensation or evaporation
  • grooves based on the set parameters are formed, and heat transfer of the heat transfer tube is achieved by increasing the surface area in the tube, the effect of fluid agitation due to the groove, and the effect of holding the liquid film between the grooves due to the capillary action of the groove.
  • the performance is improved (for example, refer to Patent Document 1).
  • the groove in the heat transfer tube of Patent Document 1 described above does not have a shape corresponding to the flow path in the heat transfer tube. For this reason, when the heat exchanger is mounted at a high density, the performance may be lowered.
  • an object of the present invention is to provide a heat exchanger, a refrigeration cycle apparatus, and an air conditioner having specifications that match a flow path in a heat transfer tube.
  • the heat exchanger includes a heat transfer tube having a groove that is a spiral recess in the tube axis direction on the tube inner surface through which the fluid passes, and a fin that contacts the heat transfer tube and promotes heat exchange of the fluid.
  • a flow path length L of a heat transfer tube in which the fluid passes between the inlet of the heat exchanger and the outlet of the heat exchanger where L ⁇ 10 m
  • the groove has a groove where the lead angle ⁇ is 25 ° ⁇ ⁇ ⁇ 45 °, and in the flow path where L> 10 m, the groove has a groove where 5 ° ⁇ ⁇ ⁇ 25 °.
  • the heat transfer tube since the heat transfer tube has a groove lead angle different depending on the flow path length L from the heat exchanger inlet to the heat exchanger outlet, It can be a heat exchanger with suitable specifications. And the efficiency of heat exchange can be improved and the APF (Annual Performance Factor) in the air conditioner can be increased.
  • APF Annual Performance Factor
  • FIG. 1 It is a figure which shows the correlation with the lead angle (theta) of the heat exchanger tube 12, and the performance of the heat exchanger tube 12 which concern on Embodiment 1 of this invention. It is the schematic which shows the correlation with lead angle (theta) and APF of the heat exchanger tube 12 which concerns on Embodiment 1 of this invention. It is a figure which shows the correlation with the groove height h of the heat exchanger tube 12 which concerns on Embodiment 2 of this invention, and the performance in the heat exchanger tube 12. FIG. It is the schematic which shows the correlation with the groove height h and APF of the heat exchanger tube 12 which concerns on Embodiment 2 of this invention. It is a figure which shows the structure of the refrigerating-cycle apparatus which concerns on Embodiment 3 of this invention.
  • FIG. 1 is a schematic diagram showing a configuration of a heat exchanger 1 according to Embodiment 1 of the present invention.
  • a heat exchanger 1 is a fin-tube heat exchanger that includes a plurality of heat exchanger bodies 10 and flow passage pipes 20.
  • heat exchange between the refrigerant passing through the heat transfer tube 12 and the air passing between the plurality of fins 11 is performed in the heat exchanger body 10 with respect to the refrigerant flowing in from the heat exchanger inlet 1A. .
  • the heat-exchanged refrigerant flows out from the heat exchanger outlet 1B.
  • the channel pipe 20 is a pipe that connects the plurality of heat exchanger bodies 10 and serves as a refrigerant channel.
  • the channel pipe 20 is a pipe having a plurality of branch numbers such as one pipe, a T-shaped pipe, and a bulge three-way pipe.
  • FIG. 2 is a schematic diagram showing the configuration of the heat exchanger body 10 according to Embodiment 1 of the present invention.
  • the heat exchanger body 10 includes a plurality of fins 11 and heat transfer tubes 12.
  • the fins 11 are, for example, substantially rectangular plate-like fins that are arranged at regular intervals.
  • Each fin 11 has a through hole so as to intersect and contact the heat transfer tube 12.
  • the heat transfer tube 12 becomes a part of the flow path in the refrigerant circuit in the refrigeration cycle apparatus, and the refrigerant flows inside the tube.
  • the heat of the refrigerant flowing inside the heat transfer tube 12 and the air flowing outside is transmitted to the fin 11.
  • the fins 11 increase the heat transfer area and can efficiently perform heat exchange between the refrigerant and the air.
  • FIG. 3 is a view for explaining the inner surface of the heat transfer tube 12 in the direction parallel to the direction of the tube axis 15 in the heat exchanger 1 according to Embodiment 1 of the present invention.
  • FIG. 4 is a figure explaining the inner surface of the heat exchanger tube 12 in the direction orthogonal to the direction of the tube axis
  • the heat transfer tube 12 of the heat exchanger 1 in Embodiment 1 has a plurality of grooves 14 in which concave portions are spirally formed on the tube inner surface side.
  • the groove 14 serves as a flow path for a refrigerant that is a fluid.
  • the grooves 14 can increase the surface area of the inner surface of the heat transfer tube 12, stir the fluid, hold a liquid film by capillary action, and promote heat transfer between the heat transfer tube 12 and the refrigerant flowing in the heat transfer tube 12. .
  • the groove 14 is processed on the inner surface of the heat transfer tube 12 so that the direction of the tube axis 15 and the direction in which the spiral groove 14 extends form a certain angle. This angle is hereinafter referred to as a lead angle ⁇ .
  • the inner surface of the tube is uneven.
  • the height of the convex portion is the groove height h of the groove 14.
  • the lead angle ⁇ of the heat transfer tube 12 is 25 ° ⁇ ⁇ ⁇ 45 ° in the heat transfer tube 12 where L ⁇ 10 m with respect to a certain flow path length L.
  • the heat transfer tube 12 is used.
  • the heat transfer tube 12 in which the lead angle ⁇ of the groove 14 satisfies 5 ° ⁇ ⁇ ⁇ 25 ° is used.
  • the length of the heat transfer tube 12 through which the refrigerant passes becomes the flow path length L.
  • the sum of the lengths L1, L2 and L3 of the heat transfer tubes 12 of the heat exchanger body 10 in the path of the flow path pipe 20 indicated by a thick line is the flow path length L.
  • FIG. 5 is a diagram showing a correlation between the lead angle ⁇ of the heat transfer tube 12 and the performance of the heat transfer tube 12 according to Embodiment 1 of the present invention.
  • the performance of the heat transfer tube 12 is represented by the in-tube heat transfer coefficient ⁇ i.
  • the heat transfer coefficient ⁇ i in the tube increases while converging as the lead angle ⁇ increases.
  • the in-pipe refrigerant pressure loss ⁇ Pref increases monotonously.
  • the efficiency is better when the heat transfer coefficient ⁇ i in the pipe is larger and the refrigerant pressure loss ⁇ Pref in the pipe is smaller. Therefore, the optimal shape of the groove 14 exists depending on the form of the heat exchanger 1.
  • FIG. 6 is a schematic diagram showing the correlation between the lead angle ⁇ and the APF of the heat transfer tube 12 according to Embodiment 1 of the present invention.
  • APF Annual Performance Factor
  • APF is an index that indicates the performance of an air conditioner during year-round use.
  • the longer the flow path length L the greater the influence of the refrigerant pressure loss ⁇ Pref in the pipe.
  • the refrigerant pressure loss ⁇ Pref in the pipe is small. Therefore, when the lead angle ⁇ is small, the APF tends to be improved.
  • the shorter the flow path length L the greater the influence of the in-tube heat transfer coefficient ⁇ i.
  • the lead angle ⁇ is large, the in-tube heat transfer coefficient ⁇ i is large. Therefore, when the lead angle ⁇ is increased, the APF tends to be improved.
  • the APF threshold is set at a lead angle ⁇ of 25 °.
  • the lead angle ⁇ of the groove 14 is 25 ° ⁇ ⁇ ⁇ 45 °
  • the lead angle ⁇ is 5 °. It is preferable to use the heat transfer tube 12 of ° ⁇ ⁇ ⁇ 25 °.
  • a heat transfer tube having an outer diameter of ⁇ 7.0 or ⁇ 6.35 is often used, but the heat transfer tube 12 of Embodiment 1 maintains the refrigerant pressure loss ⁇ Pref in the tube, The outer diameter and inner diameter can be reduced.
  • the heat transfer tube 12 having an outer diameter of ⁇ 5.0 or less, in which the refrigerant pressure loss ⁇ Pref in the tube is about twice or more can be used.
  • the volume in the tube can be reduced. Therefore, the amount of refrigerant required for the entire refrigerant circuit can be reduced.
  • the safety of the apparatus can be further improved by reducing the refrigerant.
  • the heat exchanger 1 using the heat transfer tube 12 satisfying 25 ° ⁇ ⁇ ⁇ 45 ° is configured.
  • L> 10 m the heat exchanger 1 using the heat transfer tube 12 in which the lead angle ⁇ in the groove 14 satisfies 5 ° ⁇ ⁇ ⁇ 25 ° is configured. For this reason, APF in an air conditioning apparatus can be made high.
  • Embodiment 2 FIG. ⁇ Configuration of Embodiment 2>
  • the second embodiment will be described focusing on differences from the heat transfer tube 12 of the first embodiment.
  • the heat transfer tube 12 of the second embodiment has basically the same configuration as the heat transfer tube 12 described in the first embodiment, and has a plurality of spiral grooves 14 on the inner surface.
  • the groove height h of the groove 14 is not particularly mentioned.
  • the groove height h of the groove 14 on the inner surface is such that h ⁇ 0.06 mm when L ⁇ 10 m, and 0.06 mm ⁇ h when L> 10 m. .
  • FIG. 7 is a diagram showing a correlation between the groove height h of the heat transfer tube 12 and the performance in the heat transfer tube 12 according to the second embodiment of the present invention.
  • the performance of the heat transfer tube 12 is represented by the in-tube heat transfer coefficient ⁇ i.
  • the in-tube heat transfer coefficient ⁇ i increases while converging.
  • the in-pipe refrigerant pressure loss ⁇ Pref increases monotonously.
  • the efficiency is generally better when the in-tube heat transfer coefficient ⁇ i is larger and the in-tube refrigerant pressure loss ⁇ Pref is smaller.
  • FIG. 8 is a schematic diagram showing the correlation between the groove height h of the heat transfer tube 12 and the APF according to Embodiment 2 of the present invention.
  • the longer the flow path length L the greater the influence of the refrigerant pressure loss ⁇ Pref in the pipe. Therefore, in this case, when the groove height h is small, the APF tends to be improved.
  • the shorter the flow path length L the greater the influence of the in-tube heat transfer coefficient ⁇ i. Therefore, in this case, when the groove height h is large, the APF tends to be improved.
  • the groove height h is 0.06 mm.
  • the groove height h of the groove 14 is the heat transfer tube 12 with h ⁇ 0.06 mm, and when L> 10 m, 0. It is preferable to use the heat transfer tube 12 of 06 ⁇ h.
  • the groove 14 may be a combination of the condition related to the lead angle ⁇ described in the first embodiment and the condition of the groove height h of the groove 14 in the second embodiment.
  • FIG. FIG. 9 is a diagram showing a configuration of a refrigeration cycle apparatus according to Embodiment 3 of the present invention.
  • an air conditioner 50 that cools and heats a target space will be described.
  • the air conditioner performs the steps of evaporation, compression, condensation, and expansion on the refrigerant, circulates the refrigerant while changing the phase from liquid to gas, and from gas to liquid, and transfers heat to the refrigerant. Air conditioning of the space.
  • FIG. 9 has an outdoor unit (outdoor unit) 200 and an indoor unit (indoor unit) 100.
  • the compressor 210, the four-way valve 220, the heat source side heat exchanger 230 and the expansion device 240 included in the outdoor unit 200, and the load side heat exchanger 110 included in the indoor unit 100 are connected by a gas refrigerant pipe 300 and a liquid refrigerant pipe 400.
  • a refrigerant circulation circuit is formed.
  • the refrigerant flow during the cooling operation is indicated by a solid arrow
  • the refrigerant flow during the heating operation is indicated by a dotted arrow.
  • the outdoor unit 200 includes a compressor 210, a four-way valve 220, a heat source side heat exchanger 230, an expansion device 240, and a heat source side blower 250.
  • the compressor 210 compresses and discharges the sucked refrigerant.
  • the capacity of the compressor 210 may be changed by arbitrarily changing the operation frequency by using, for example, an inverter circuit.
  • the four-way valve 220 is a valve that switches the flow of the refrigerant between, for example, a cooling operation and a heating operation.
  • the heat source side heat exchanger 230 in Embodiment 3 performs heat exchange between the refrigerant and air (outdoor air). For example, it functions as an evaporator during heating operation, evaporating and evaporating the refrigerant. Moreover, it functions as a condenser during the cooling operation, and condenses and liquefies the refrigerant.
  • the heat source side blower 250 sends air into the heat source side heat exchanger 230.
  • the heat source side blower 250 is controlled by the control device 60A.
  • a throttling device 240 such as an expansion valve (flow rate control means) decompresses the refrigerant to expand it.
  • the opening degree is adjusted based on an instruction from the control device 60A.
  • the indoor unit 100 has a load side heat exchanger 110 and a load side blower 120.
  • the load-side heat exchanger 110 performs heat exchange between air to be air-conditioned and a refrigerant. During heating operation, it functions as a condenser and condenses and liquefies the refrigerant. Moreover, it functions as an evaporator during cooling operation, evaporating and evaporating the refrigerant.
  • the heat exchanger 1 in Embodiment 1 and Embodiment 2 is used for the load-side heat exchanger 110.
  • the load side heat exchanger 110 it is not limited to the load side heat exchanger 110, but may be used for the heat source side heat exchanger 230, and is used for at least one of the heat exchangers 1 serving as a condenser and an evaporator.
  • the heat exchanger 1 for the load-side heat exchanger 110, it is possible to provide a high-performance air conditioner with good heat exchange efficiency.
  • the load side blower 120 sends air into the load side heat exchanger 110.
  • the load-side fan 120 is controlled by the control device 60A.
  • the compressor 210, the four-way valve 220, the expansion device 240, the heat source side blower 250, the load side blower 120, various sensors, and the like are connected to the control device 60A and the control device 60B.
  • the control device 60A and the control device 60B control operations of devices such as the compressor 210 based on signals sent from various sensors.
  • the cooling operation and the heating operation are switched.
  • the high-pressure and high-temperature gaseous refrigerant discharged from the compressor 210 flows into the heat source side heat exchanger 230 via the four-way valve 220 and condenses by heat exchange with the outside air supplied by the heat source side blower 250.
  • the refrigerant becomes a high-pressure liquid state and flows out of the heat source side heat exchanger 230.
  • the high-pressure liquid refrigerant flowing out of the heat source side heat exchanger 230 flows into the expansion device 240 and becomes a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant flowing out of the expansion device 240 flows into the load-side heat exchanger 110 and evaporates by heat exchange with the indoor air supplied by the load-side fan 120, thereby causing a low-pressure gas state. And flows out of the load-side heat exchanger 110.
  • the low-pressure gaseous refrigerant flowing out from the load-side heat exchanger 110 is sucked into the compressor 210 through the four-way valve 220.
  • the high-pressure and high-temperature gas refrigerant discharged from the compressor 210 flows into the load-side heat exchanger 110 via the four-way valve 220.
  • the refrigerant is condensed by heat exchange with room air supplied by the load-side fan 120, thereby becoming a high-pressure liquid refrigerant and flows out of the load-side heat exchanger 110.
  • the high-pressure liquid refrigerant flowing out of the load-side heat exchanger 110 flows into the expansion device 240 and becomes a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant flowing out of the expansion device 240 flows into the heat source side heat exchanger 230 and evaporates by heat exchange with the outside air supplied by the heat source side blower 250, whereby the low pressure gas refrigerant. And flows out of the heat source side heat exchanger 230.
  • the low-pressure gaseous refrigerant flowing out from the heat source side heat exchanger 230 is sucked into the compressor 210 via the four-way valve 220.
  • the refrigerating machine oil used in the compressor 210 it is preferable to use an incompatible oil having incompatibility such as HAB oil, for example, from the viewpoint of melting of the refrigerant and replacement.
  • HAB oil incompatible oil having incompatibility
  • the heat transfer tube 12 having a low pressure loss in the tube. Therefore, by using the heat exchanger 1 according to the first embodiment and the second embodiment, it is possible to provide the air conditioner 50 that can ensure high quality with high performance.
  • an R32 refrigerant is generally used in a room air conditioner.
  • R290 can be cited as a candidate.
  • R290 has a larger refrigerant pressure loss ⁇ Pref in the pipe than R32.
  • R290 is a highly flammable refrigerant, there is a possibility that it will burn if the amount enclosed is large. Therefore, the heat exchanger 1 described in the first embodiment and the second embodiment described above can compensate for the loss due to the refrigerant pressure loss ⁇ Pref in the pipe due to R290.
  • the heat exchanger 1 can reduce the pipe internal volume in the unit, the amount of refrigerant can be reduced. Therefore, it is possible to provide a refrigeration cycle apparatus that can ensure high performance and quality.

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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)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

Cet échangeur de chaleur comprend un corps d'échangeur de chaleur ayant : un tuyau de transmission de chaleur à travers lequel passe un fluide et qui a une rainure formée dans sa surface interne, la rainure étant un évidement s'étendant en spirale dans la direction de l'axe de tuyau; et une ailette qui est en contact avec le tuyau de transmission de chaleur pour favoriser l'échange de chaleur du fluide. Si une longueur de chemin d'écoulement L, qui est la longueur du tuyau de transmission de chaleur, de l'entrée d'échangeur de chaleur à la sortie d'échangeur de chaleur entre lesquelles s'écoule le fluide, n'est pas supérieure à 10 m, l'angle de fil θ formé entre l'axe de tuyau et la rainure satisfait à 25°≤θ≤45°, et si la longueur de chemin d'écoulement L est supérieure à 10 m, l'angle de fil θ satisfait à 5°≤θ≤25°.
PCT/JP2018/011044 2018-03-20 2018-03-20 Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation Ceased WO2019180817A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/JP2018/011044 WO2019180817A1 (fr) 2018-03-20 2018-03-20 Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation
JP2020507166A JP6925508B2 (ja) 2018-03-20 2018-03-20 熱交換器、冷凍サイクル装置および空気調和装置
CN201880091134.5A CN111886459A (zh) 2018-03-20 2018-03-20 热交换器、制冷循环装置和空调装置
EP18911206.3A EP3770535A4 (fr) 2018-03-20 2018-03-20 Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/011044 WO2019180817A1 (fr) 2018-03-20 2018-03-20 Échangeur de chaleur, dispositif à cycle frigorifique, et dispositif de climatisation

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WO2019180817A1 true WO2019180817A1 (fr) 2019-09-26

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EP (1) EP3770535A4 (fr)
JP (1) JP6925508B2 (fr)
CN (1) CN111886459A (fr)
WO (1) WO2019180817A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022079763A1 (fr) 2020-10-12 2022-04-21 三菱電機株式会社 Dispositif à cycle de réfrigération, climatiseur et échangeur de chaleur

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WO1996012151A1 (fr) * 1994-10-18 1996-04-25 The University Of Manchester Institute Of Science And Technology Tube de transfert thermique
JPH11264630A (ja) * 1998-03-19 1999-09-28 Hitachi Ltd 空気調和機
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