WO2014125997A1 - Dispositif d'échange de chaleur, et dispositif à cycles de réfrigération équipé de celui-ci - Google Patents

Dispositif d'échange de chaleur, et dispositif à cycles de réfrigération équipé de celui-ci Download PDF

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Publication number
WO2014125997A1
WO2014125997A1 PCT/JP2014/052790 JP2014052790W WO2014125997A1 WO 2014125997 A1 WO2014125997 A1 WO 2014125997A1 JP 2014052790 W JP2014052790 W JP 2014052790W WO 2014125997 A1 WO2014125997 A1 WO 2014125997A1
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WO
WIPO (PCT)
Prior art keywords
heat transfer
transfer tube
tube
groove
heat
Prior art date
Application number
PCT/JP2014/052790
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English (en)
Japanese (ja)
Inventor
相武 李
牧野　浩招
早丸　靖英
大輔 杉山
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 JP2015500210A priority Critical patent/JP6104357B2/ja
Priority to CN201420065077.2U priority patent/CN203771807U/zh
Publication of WO2014125997A1 publication Critical patent/WO2014125997A1/fr

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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
    • F28F1/10—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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/04—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by preventing the formation of continuous films of condensate on heat-exchange surfaces, e.g. by promoting droplet formation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary

Definitions

  • the present invention relates to a heat exchange apparatus including a heat transfer tube having a groove on the inner surface of the tube.
  • a heat exchanger used in a refrigeration apparatus an air conditioner, or a heat pump
  • a plurality of fins arranged at predetermined intervals are provided with through holes, and heat transfer tubes are disposed through the through holes.
  • the heat transfer tubes are arranged in a plurality of rows in the airflow direction, and grooves are formed on the inner surface.
  • the heat transfer tube becomes a part of the refrigerant circuit in the refrigeration cycle apparatus, and the refrigerant (fluid) flows through the inside of the tube.
  • the groove on the inner surface of the tube is processed in a spiral shape so that the tube axis direction and the direction in which the groove extends form a certain angle.
  • the inner surface of the tube can be made uneven.
  • the space of the recessed portion is referred to as a groove portion
  • the protruding portion formed by the side wall of the adjacent groove is referred to as a peak portion.
  • the inner groove pitch and the groove lead angle of the heat transfer tube on the upstream side of the airflow are made smaller than the inner surface groove pitch and the groove lead angle of the heat transfer tube on the downstream side of the airflow.
  • the heat transfer promotion effect is improved.
  • the groove pitch and groove lead angle of the heat transfer tube on the upstream side of the airflow are made smaller than the inner surface groove pitch and groove lead angle of the heat transfer tube on the downstream side of the airflow, the amount of liquid refrigerant retained
  • the heat transfer coefficient in the heat transfer tube on the upstream side of the air flow is lowered, and the coefficient of performance (COP) is lowered.
  • the present invention has been made to solve the above-described problems, and can improve the heat transfer rate in the pipe of the heat exchanger and obtain a preset heat transfer performance without increasing the pressure loss in the pipe.
  • An object is to provide a heat exchange device.
  • the heat exchange device includes a first heat transfer tube disposed on the upstream side with respect to the gas flow, and a second heat transfer tube disposed side by side with the first heat transfer tube on the downstream side of the first heat transfer tube.
  • the first heat transfer tube and the second heat transfer tube have a groove on the inner surface of the tube, and the first heat transfer tube has an area Aa and an outer diameter Do of the groove portion in a plane orthogonal to the tube axis.
  • the ratio (Aa / Do) is larger than the ratio (Ab / Do) between the area Ab of the groove and the outer diameter Do in a plane orthogonal to the tube axis of the second heat transfer tube.
  • the first heat transfer tube disposed on the upstream side with respect to the gas flow and the second heat exchanger disposed side by side with the first heat transfer tube on the downstream side of the first heat transfer tube.
  • a heat transfer tube, the first heat transfer tube and the second heat transfer tube have grooves on the inner surface of the tube, and the first heat transfer tube has a ratio between the area Aa of the groove portion on the plane perpendicular to the tube axis and the outer diameter Do. Since (Aa / Do) is formed larger than the ratio (Ab / Do) of the area Ab of the groove part to the outer diameter Do in the plane orthogonal to the tube axis of the second heat transfer tube, the liquid refrigerant held in the groove part Will increase. For this reason, compared with a conventional heat transfer tube, the heat transfer performance in the tube for condensation / evaporation can be improved without increasing the pressure loss, and the heat exchange efficiency is improved.
  • FIG. 1 is a diagram showing the flow of refrigerant in the heat exchange device according to Embodiment 1 of the present invention.
  • a heat exchange device 1 is a fin tube type heat exchanger widely used as an evaporator or a condenser of a refrigeration device or an air conditioner.
  • the flow direction of the gas flowing between the plurality of fins 10 includes a heat exchanger in which a plurality of heat transfer tubes 20 having grooves on the tube inner surface are inserted into the plurality of fins 10.
  • a plurality of rows of heat exchangers configured by the plurality of rows are provided.
  • the main heat exchanger 1 ⁇ / b> A and the sub heat exchanger 1 ⁇ / b> B are connected via a dehumidification valve 30.
  • the dehumidifying valve 30 is provided to use a part of the heat exchanger as a condenser and the other as an evaporator during dehumidification (dehumidification while heating the room).
  • the heat transfer tube 20 becomes a part of the refrigerant circuit in the refrigeration cycle apparatus, and the refrigerant flows inside the tube.
  • the heat transfer tube 20 transfers the heat of the refrigerant flowing inside to the air flowing outside through the fins 10, thereby expanding the heat transfer area serving as a contact surface with the air, and exchanging heat between the refrigerant and the air. Do it efficiently.
  • FIG. 2 is a partially enlarged view of a vertical cross section of the heat exchange device according to Embodiment 1 of the present invention as viewed from the side, and shows the shape of the inner surface of the heat transfer tube 20 and the groove pitch in an enlarged manner.
  • FIG. 3 is an explanatory diagram of the liquid refrigerant holding effect between the groove portions due to the capillary action of the groove portions in the first row of heat transfer tubes of the heat exchange device according to Embodiment 1 of the present invention.
  • the first row from the windward side as the first heat transfer tube shown in FIG.
  • the ratio (Aa / Do) between the area Aa of the groove 21a (hereinafter referred to as “the area Aa of the groove 21a of the heat transfer tube 20A”) and the outer diameter Do in the plane orthogonal to the tube axis of the heat transfer tube 20A is the second heat transfer tube.
  • the ratio (Aa / Do) of the heat transfer tubes 20A in the first row from the windward side is set to the ratio (Aa / Do) of the heat transfer tubes 20B in the second and subsequent rows from the windward side ( (Ab / Do).
  • the temperature difference between the air and the refrigerant is large.
  • the heat transfer tubes 20A in the first row from the windward side are regions where a large amount of liquid refrigerant exists. For this reason, when the ratio (Aa / Do) of the area Aa of the groove part 21b of the heat transfer tube 20A in the first row and the outer diameter Do is increased, the peak part 22a between the groove parts is accompanied by the capillary action of the groove part 21a as shown in FIG. The amount of liquid refrigerant 40 held in is increased, and the heat exchange efficiency is improved through the peak portions 22a formed by the side walls of the adjacent groove portions 21a.
  • the temperature difference between the air and the refrigerant is small, and there is a small amount of liquid refrigerant, and the liquid refrigerant 40 (see FIG. 3) held in the groove 21b. Less. For this reason, by reducing the ratio (Ab / Do) between the area Ab of the groove 21b of the heat transfer tube 20B in the second row and the outer diameter Do (Ab / Do), the peak portion 22b between the grooves along the capillary action of the groove 21b.
  • the liquid refrigerant 40 to be held can be relatively increased, and the heat exchange efficiency is improved through the crests 22b formed by the side walls of the adjacent grooves 21b.
  • the ratio (Aa / Do) of the area Aa of the groove 21a of the heat transfer tube 20A to the outer diameter Do is in the range of 0.0075 (mm 2 / mm) to 0.0125 (mm 2 / mm). It is formed to become.
  • the ratio (Ab / Do) of the area Ab of the groove 21b of the heat transfer tube 20B to the outer diameter Do (Ab / Do) is 0.0028 (mm 2 / mm) to 0.0074. It is formed to be in the range of (mm 2 / mm).
  • the ratio (Aa / Do) between the area Aa and the outer diameter Do of the groove portion 21a of the heat transfer tube 20A in the first row from the windward side is 0.0075 (mm 2 / mm) to 0.
  • the range of 0.125 (mm 2 / mm) is set so that the ratio (Aa / Do) between the area Aa and the outer diameter Do of the groove portion 21a of the heat transfer tube 20A in the first row is 0.0075 (mm 2 / mm
  • the ratio (Aa / Do) of the area Aa of the groove portion 21a of the heat transfer tube 20A in the first row to the outer diameter Do is greater than 0.0125 (mm 2 / mm)
  • the liquid refrigerant holding effect is reduced, and the inside of the tube This is because the heat transfer performance decreases as a whole.
  • the ratio (Ab / Do) of the area Ab of the groove 21b of the heat transfer tube 20B in the second row from the windward side to the outer diameter Do (Ab / Do) is 0.0028 (mm 2 / mm) to 0.0074.
  • the range (mm 2 / mm) is set so that the ratio (Ab / Do) between the area Ab and the outer diameter Do of the groove 21b of the heat transfer tube 20B in the second row from the windward side is 0.0028 (mm 2 / mm). If it is smaller than (mm), the liquid refrigerant held in the groove portion 21b is reduced, the liquid film thickness to the peak portion 22b is increased, and the heat transfer performance in the tube is lowered as a whole.
  • the ratio (Ab / Do) of the area Ab of the groove part 21b of the heat transfer tube 20B in the second row from the windward side to the outer diameter Do is larger than 0.0074 (mm 2 / mm)
  • the liquid refrigerant holding effect is lowered. This is because the heat transfer performance in the tube decreases as a whole.
  • the heat exchange device 1 of the first embodiment in the two or more rows of indoor side heat exchangers in which the plurality of heat transfer tubes 20 are inserted into the plurality of fins 10, Between the area Aa and the outer diameter Do of the groove portion 21a of the heat transfer tube 20A in the first row from the windward side in the section from the windward side to the dehumidifying valve 30 or before the dehumidifying valve 30 in the heating operation. Since the ratio (Aa / Do) is larger than the ratio (Ab / Do) between the area Ab of the groove 21b of the heat transfer tube 20B in the second and subsequent rows from the windward side and the outer diameter Do, the heat transfer performance in the tube is improved.
  • the heat exchange rate (ratio of the amount of heat before and after passing through the heat transfer tube) can be increased. Therefore, energy saving can be achieved. Further, it is possible to reduce the size of the refrigerant circuit while reducing the amount of refrigerant and maintaining the efficiency.
  • the area Aa / outer diameter Do of the groove portion 21a of the heat transfer tube 20A in the first row is 0.0075, 0.0095, 0.0115, 0.0125 (mm 2 / mm)
  • the second row The heat exchange devices 1 of Examples 1 to 4 in which the area Ab / outer diameter Do of the groove portion 21b of the heat transfer tube 20B was 0.0035 (mm 2 / mm) were produced (Examples 1 to 4).
  • the area Aa / outer diameter Do of the groove portion 21a of the heat transfer tube 20A in the first row is 0.005, 0.035 (mm 2 / mm), and the area of the groove portion 21b of the heat transfer tube 20B in the second row.
  • a heat exchange device having an Ab / outer diameter Do of 0.0035 (mm 2 / mm) was produced (Comparative Examples 1 and 2).
  • the heat exchange devices 1 of Examples 1 to 4 each had a higher heat exchange rate than the heat exchangers of Comparative Examples 1 and 2, and the heat transfer performance in the tube was improved.
  • the area Aa / outer diameter Do of the groove 21a of the first row of heat transfer tubes 20A is 0.0095 (mm 2 / mm), the area Ab / outside of the groove 21b of the second row of heat transfer tubes 20B.
  • the heat exchange devices 1 of Examples 5 to 8 having a diameter Do of 0.0028, 0.0035, 0.005, and 0.0074 (mm 2 / mm) were produced.
  • the area Aa / outer diameter Do of the groove portion 21a of the heat transfer tube 20A in the first row is 0.0095 (mm 2 / mm), and the area Ab / outer diameter of the groove portion 21b of the heat transfer tube 20B in the second row.
  • Heat exchange devices having Do of 0.0025 and 0.008 (mm 2 / mm) were produced (Comparative Examples 3 and 4).
  • the main heat exchanger 1A and the sub heat exchanger 1B are both configured by a group of heat exchangers configured in a plurality of rows, that is, the fins 10 are divided in a plurality of rows in the gas flow direction.
  • the present invention is not limited to this.
  • it is good also as a structure which does not divide
  • FIG. 4 is a refrigerant circuit diagram of an air conditioner according to Embodiment 2 of the present invention, in which the heat exchange device described in Embodiment 1 is used as an indoor heat exchanger.
  • a compressor 61, a four-way valve 62, an outdoor heat exchanger 63, a decompressor 64, and an indoor heat exchanger 65 are connected in a closed loop by a refrigerant pipe 70, and the indoor unit 50
  • a gas valve 68 and a liquid valve 69 are disposed between the outdoor unit 60 and the outdoor unit 60.
  • the outdoor heat exchanger 63 is provided with an outdoor fan 66
  • the indoor heat exchanger 65 is provided with an indoor fan 67.
  • the low-pressure and low-temperature gas refrigerant is compressed into the high-temperature and high-pressure gas refrigerant by the compressor 61 of the outdoor unit 60 and sent to the four-way valve 62. And it guide
  • the high-pressure liquid refrigerant exiting from the outdoor heat exchanger 63 is converted into a low-pressure and low-temperature gas-liquid two-phase refrigerant by the decompressor 64 and led to the indoor heat exchanger 65 of the indoor unit 50 through the liquid valve 69.
  • the heat in the indoor air is absorbed and the refrigerant evaporates to become a low-pressure and low-temperature gas refrigerant, and the cooling operation is performed (the indoor heat exchanger 65 acts as an evaporator).
  • the low-pressure and low-temperature gas refrigerant is guided to the compressor 61 through the gas valve 68 and the four-way valve 62 to perform the refrigerant cycle operation.
  • the indoor heat exchanger 65 acts as a condenser and the outdoor heat exchanger 63 acts as an evaporator by switching the four-way valve 62 to make the refrigerant flow in the opposite direction to that in the cooling operation. The rest is the same as in the cooling operation.
  • the heat exchange device 1 according to the first embodiment is used as the indoor heat exchanger 65, the heat transfer performance in the pipe of the indoor heat exchanger 65 can be improved.
  • the exchange rate ratio of the amount of heat before and after passing through the heat transfer tube
  • energy saving can be achieved.
  • the application to the refrigeration apparatus or the air conditioner has been described with respect to the heat exchange apparatus according to the present invention.
  • the present invention is not limited to these apparatuses.
  • the present invention can also be applied to other refrigeration cycle apparatuses having a heat exchanger such as an evaporator and a condenser that constitute a refrigerant circuit like a heat pump apparatus.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

La présente invention, qui permet d'accroître l'efficacité de transfert de chaleur dans des tubes pendant la condensation et l'évaporation sans accroître la perte de pression, consiste à prévoir au moins un premier tube (20A) de transfert de chaleur, placé en amont de l'écoulement d'un gaz et un deuxième tube (20B) de transfert de chaleur, placé le long du premier tube (20A) de transfert de chaleur, plus en aval que ledit premier tube (20A)de transfert de chaleur ; à former des rainures sur le premier tube (20A) de transfert de chaleur et le deuxième tube (20B) de transfert de chaleur, sur la surface intérieure de ceux-ci ; et à faire en sorte que le rapport (Aa/Do) de la surface (Aa) par rapport au diamètre extérieur (Do) de parties rainures (21a), formées sur le premier tube de transfert de chaleur (20A), dans un plan perpendiculaire à l'axe du tube, soit supérieur au rapport (Ab/Do) de la surface (Ab) par rapport au diamètre extérieur (Do) de parties rainures (21b), formées sur le deuxième tube de transfert de chaleur (20B), dans un plan perpendiculaire à l'axe du tube.
PCT/JP2014/052790 2013-02-14 2014-02-06 Dispositif d'échange de chaleur, et dispositif à cycles de réfrigération équipé de celui-ci WO2014125997A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2015500210A JP6104357B2 (ja) 2013-02-14 2014-02-06 熱交換装置およびこれを備えた冷凍サイクル装置
CN201420065077.2U CN203771807U (zh) 2013-02-14 2014-02-14 换热装置及具有该换热装置的制冷循环装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JPPCT/JP2013/053577 2013-02-14
PCT/JP2013/053577 WO2014125603A1 (fr) 2013-02-14 2013-02-14 Dispositif d'échange de chaleur, et dispositif à cycles de réfrigération équipé de celui-ci

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WO2014125997A1 true WO2014125997A1 (fr) 2014-08-21

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PCT/JP2013/053577 WO2014125603A1 (fr) 2013-02-14 2013-02-14 Dispositif d'échange de chaleur, et dispositif à cycles de réfrigération équipé de celui-ci
PCT/JP2014/052790 WO2014125997A1 (fr) 2013-02-14 2014-02-06 Dispositif d'échange de chaleur, et dispositif à cycles de réfrigération équipé de celui-ci

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2934733T3 (es) 2015-12-29 2023-02-24 Zuta Core Ltd Sistema de gestión térmica basado en vacío
EP3546875B1 (fr) 2016-11-28 2020-05-27 Mitsubishi Electric Corporation Échangeur de chaleur, dispositif à cycle de réfrigération et procédé de fabrication d'échangeur de chaleur
WO2020202492A1 (fr) * 2019-04-03 2020-10-08 三菱電機株式会社 Échangeur de chaleur et climatiseur

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000329486A (ja) * 1999-05-17 2000-11-30 Matsushita Electric Ind Co Ltd フィン付き熱交換器
JP2005083715A (ja) * 2003-09-11 2005-03-31 Sharp Corp 熱交換器
JP2009127882A (ja) * 2007-11-20 2009-06-11 Mitsubishi Electric Corp 熱交換器、室内機及び空気調和機

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11257800A (ja) * 1998-03-09 1999-09-24 Sanyo Electric Co Ltd 熱交換器及びその熱交換器を備えた空気調和装置
JP5197820B2 (ja) * 2011-09-12 2013-05-15 三菱電機株式会社 冷凍サイクル装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000329486A (ja) * 1999-05-17 2000-11-30 Matsushita Electric Ind Co Ltd フィン付き熱交換器
JP2005083715A (ja) * 2003-09-11 2005-03-31 Sharp Corp 熱交換器
JP2009127882A (ja) * 2007-11-20 2009-06-11 Mitsubishi Electric Corp 熱交換器、室内機及び空気調和機

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WO2014125603A1 (fr) 2014-08-21
JP6104357B2 (ja) 2017-03-29

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