WO2014125997A1 - Heat exchange device and refrigeration cycle device equipped with same - Google Patents

Heat exchange device and refrigeration cycle device equipped with same 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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Prior art keywords
heat transfer
transfer tube
tube
groove
heat
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PCT/JP2014/052790
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French (fr)
Japanese (ja)
Inventor
相武 李
牧野　浩招
早丸　靖英
大輔 杉山
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三菱電機株式会社
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Priority to JP2015500210A priority Critical patent/JP6104357B2/en
Priority to CN201420065077.2U priority patent/CN203771807U/en
Publication of WO2014125997A1 publication Critical patent/WO2014125997A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—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)
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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

The present invention enables the increase of in-tube heat transfer performance during condensation and evaporation without increasing pressure loss by providing at least a first heat transfer tube (20A) disposed on the upstream side of the flow of a gas and a second heat transfer tube (20B) disposed alongside the first heat transfer tube (20A) further on the downstream side than the first heat transfer tube (20A), providing the first heat transfer tube (20A) and the second heat transfer tube (20B) with grooves on the inner surface thereof, and forming a larger ratio (Aa/Do) of the area (Aa) to the outer diameter (Do) of groove sections (21a) on the first heat transfer tube (20A) in a plane perpendicular to the axis of the tube than the ratio (Ab/Do) of the area (Ab) to the outer diameter (Do) of groove sections (21b) on the second heat transfer tube (20B) in a plane perpendicular to the axis of the tube.

Description

熱交換装置およびこれを備えた冷凍サイクル装置Heat exchange device and refrigeration cycle device provided with the same
　本発明は、管内面に溝を有する伝熱管を備えた熱交換装置に関する。 The present invention relates to a heat exchange apparatus including a heat transfer tube having a groove on the inner surface of the tube.
　従来、冷凍装置、空気調和装置、又はヒートポンプに用いる熱交換器では、一般に、所定の間隔で複数並べたフィンに貫通穴が設けられ、貫通穴に伝熱管が貫通して配置されている。伝熱管は、気流方向に複数列配置され、内面に溝が形成されている。伝熱管は、冷凍サイクル装置における冷媒回路の一部となり、管内部を冷媒（流体）が流れるようにしている。 Conventionally, in a heat exchanger used in a refrigeration apparatus, an air conditioner, or a heat pump, generally, 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.
　管内面の溝は、管軸方向と溝が延びる方向とが一定の角度をなすように螺旋状に加工されている。溝を形成することにより管内面に凹凸ができるが、ここでは、凹部の空間を溝部と称し、隣り合う溝の側壁によって形成される凸部分を山部と称する。 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. By forming the groove, the inner surface of the tube can be made uneven. Here, the space of the recessed portion is referred to as a groove portion, and the protruding portion formed by the side wall of the adjacent groove is referred to as a peak portion.
　そして、このような伝熱管を流れる冷媒は、伝熱管外側を流れる流体（例えば空気）との熱交換により相変化（凝縮又は蒸発）する。そして、この相変化を効率よく行わせるために、管内の表面積増加、溝部による流体攪拌効果、溝部の毛細管作用に伴う溝部間の液冷媒保持効果を利用して、伝熱管の伝熱性能の改善を図っている（例えば、特許文献１）。 And the refrigerant flowing through such a heat transfer tube undergoes phase change (condensation or evaporation) by heat exchange with a fluid (for example, air) flowing outside the heat transfer tube. In order to efficiently perform this phase change, the heat transfer performance of the heat transfer tube is improved by utilizing the surface area increase in the tube, the fluid stirring effect by the groove, and the liquid refrigerant holding effect between the grooves due to the capillary action of the groove. (For example, Patent Document 1).
特開平５－３２２４７１号公報（図１）JP-A-5-322471 (FIG. 1)
　ところで、前述のような熱交換器では、気流上流側の伝熱管の内面溝ピッチと溝リード角を、気流下流側の伝熱管の内面溝ピッチと溝リード角に比べて小さくすることで、溝の伝熱促進効果を高めるようにしている。しかしながら、このように気流上流側の伝熱管の溝ピッチと溝リード角を、気流下流側の伝熱管の内面溝ピッチと溝リード角に比べて小さくした熱交換器においては、液冷媒の保持量が小さくなり、気流上流側の伝熱管の管内熱伝達率が低下し、成績係数（ＣＯＰ）が低下するという難点があった。 By the way, in the heat exchanger as described above, 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. However, in the heat exchanger in which 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 However, 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.
　本発明は前記の課題を解決するためになされたもので、熱交換器の管内熱伝熱率を向上させ、管内圧力損失を増加させずに、予め設定された伝熱性能を得ることができる熱交換装置を提供することを目的とする。 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.
　本発明に係る熱交換装置は、気体の流れに対して上流側に配置された第１伝熱管と、第１伝熱管よりも下流側にこの第１伝熱管と並んで配置された第２伝熱管とを少なくとも有する熱交換装置において、第１伝熱管及び第２伝熱管は管内面に溝を有し、第１伝熱管は、管軸に直交する平面における溝部の面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）が、第２伝熱管の管軸に直交する平面における溝部の面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）より大きく形成されたものである。 The heat exchange device according to the present invention 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. In the heat exchange device having at least a heat 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.
　本発明の熱交換装置によれば、気体の流れに対して上流側に配置された第１伝熱管と、第１伝熱管よりも下流側にこの第１伝熱管と並んで配置された第２伝熱管とを少なくとも有し、第１伝熱管及び第２伝熱管は管内面に溝を有し、第１伝熱管は、管軸に直交する平面における溝部の面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）が、第２伝熱管の管軸に直交する平面における溝部の面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）より大きく形成されているので、溝部に保持される液冷媒が多くなる。このため、従来の伝熱管に比べて、圧力損失を増加させずに、凝縮・蒸発の管内伝熱性能を高めることができ、熱交換効率が良くなる。 According to the heat exchange device of the present invention, 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.
本発明の実施の形態１に係る熱交換装置の冷媒の流れを示す図である。It is a figure which shows the flow of the refrigerant | coolant of the heat exchange apparatus which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る熱交換装置を側面側から見た鉛直方向断面の部分拡大図である。It is the elements on larger scale of the perpendicular direction cross section which looked at the heat exchange apparatus which concerns on Embodiment 1 of this invention from the side surface side. 本発明の実施の形態１に係る熱交換装置の１列目の伝熱管内の溝部の毛細管作用に伴う溝部間の液冷媒保持効果の説明図である。It is explanatory drawing of the liquid refrigerant holding effect between the groove parts accompanying the capillary action of the groove part in the 1st row heat exchanger tube of the heat exchange apparatus which concerns on Embodiment 1 of this invention. 本発明の実施の形態２に係る空気調和機の冷媒回路図である。It is a refrigerant circuit figure of the air conditioner which concerns on Embodiment 2 of this invention.
実施の形態１．
　図１は本発明の実施の形態１に係る熱交換装置の冷媒の流れを示す図である。図１において、熱交換装置１は、冷凍装置または空気調和装置の蒸発器、凝縮器として広く利用されているフィンチューブ式の熱交換器である。 Embodiment 1 FIG.
FIG. 1 is a diagram showing the flow of refrigerant in the heat exchange device according to Embodiment 1 of the present invention. In FIG. 1, 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.
　本実施の形態１の熱交換装置１は、管内面に溝を有する複数の伝熱管２０を複数のフィン１０に挿通させてなる熱交換器を、複数のフィン１０の間を流れる気体の流れ方向に複数列設け、さらにこの複数列で構成される熱交換器の群を少なくとも２つ（主熱交換器１Ａと副熱交換器１Ｂ）備えている。そして、これら主熱交換器１Ａと副熱交換器１Ｂとの間が除湿弁３０を介して接続されている。なお、除湿弁３０は、除湿時（室内を加熱しながらの除湿）に、熱交換器の一部を凝縮器、他を蒸発器として用いるために設けられている。
　伝熱管２０は、冷凍サイクル装置における冷媒回路の一部となり、管内部を冷媒が流れる。伝熱管２０は、内部を流れる冷媒の熱を、外部を流れる空気にフィン１０を介して伝えることで、空気との接触面となる伝熱面積を拡げ、冷媒と空気との間の熱交換を効率よく行う。 In the heat exchange device 1 according to the first embodiment, 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 (a main heat exchanger 1A and a sub heat exchanger 1B) 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.
　図２は本発明の実施の形態１に係る熱交換装置を側面側から見た鉛直方向断面の部分拡大図であり、伝熱管２０の管内面の形状と、溝ピッチを拡大して示している。図３は本発明の実施の形態１に係る熱交換装置の１列目の伝熱管内の溝部の毛細管作用に伴う溝部間の液冷媒保持効果の説明図である。冷房運転で冷媒入口から除湿弁３０に至る前までの区間、または暖房運転で除湿弁３０の後から冷媒出口までの区間で、図２に示す第１伝熱管である風上側から１列目の伝熱管２０Ａの管軸に直交する平面における溝部２１ａの面積Ａａ（以下、「伝熱管２０Ａの溝部２１ａの面積Ａａ」という）と外径Ｄｏとの比（Ａａ／Ｄｏ）は、第２伝熱管である風上側から２列目以降の伝熱管２０Ｂの管軸に直交する平面における溝部２１ｂの面積Ａｂ（以下、「伝熱管２０Ｂの溝部２１ｂの面積Ａｂ」という）と外径Ｄｏとの比（Ａｂ／Ｄｏ）より大きく形成されている。すなわち、風上側から１列目の伝熱管２０Ａの溝部２１ａの溝ピッチＰａを、風上側から２列目以降の伝熱管２０Ｂの溝部２１ｂの溝ピッチＰｂより大きくすることで、これら伝熱管２０Ａ，２０Ｂの溝部２１，２１ｂの溝高さは変えずに、風上側から１列目の伝熱管２０Ａの前記比（Ａａ／Ｄｏ）を、風上側から２列目以降の伝熱管２０Ｂの前記比（Ａｂ／Ｄｏ）より大きくしている。
　風上側から１列目の伝熱管２０Ａでは、空気と冷媒との温度差が大きい。つまり、風上側から１列目の伝熱管２０Ａは、液冷媒が多く存在する領域である。このため、１列目の伝熱管２０Ａの溝部２１ｂの面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）を大きくすると、図３のように溝部２１ａの毛細管作用に伴い溝部間の山部２２ａにて保持される液冷媒４０が多くなり、隣り合う溝部２１ａの側壁によって形成される山部２２ａを通して熱交換効率が良くなる。
　一方、風上側から２列目以降の伝熱管２０Ｂでは、空気と冷媒との温度差が小さく、液冷媒が少なく存在する領域であり、溝部２１ｂに保持される液冷媒４０（図３参照）が少なくなる。このため、２列目以降の伝熱管２０Ｂの溝部２１ｂの面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）を小さくすることで、溝部２１ｂの毛細管作用に伴い溝部間の山部２２ｂにて保持される液冷媒４０を相対的に多くすることができ、隣り合う溝部２１ｂの側壁によって形成される山部２２ｂを通して熱交換効率が良くなる。 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. In the section from the refrigerant inlet to the dehumidifying valve 30 in the cooling operation, or the section from after the dehumidifying valve 30 to the refrigerant outlet in the heating operation, 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 of the area Ab of the groove 21b (hereinafter referred to as “the area Ab of the groove 21b of the heat transfer tube 20B”) to the outer diameter Do in a plane perpendicular to the tube axis of the heat transfer tubes 20B in the second and subsequent rows from the windward side ( It is formed larger than (Ab / Do). That is, by making the groove pitch Pa of the groove portion 21a of the first row of heat transfer tubes 20A from the windward side larger than the groove pitch Pb of the groove portion 21b of the heat transfer tubes 20B of the second and subsequent rows from the windward side, these heat transfer tubes 20A, Without changing the groove height of the groove portions 21 and 21b of 20B, 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).
In the heat transfer tubes 20A in the first row from the windward side, the temperature difference between the air and the refrigerant is large. That is, 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.
On the other hand, in the heat transfer tubes 20B in the second and subsequent rows from the windward side, 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.
　本実施の形態１の熱交換装置１において、冷房運転で冷媒入口から除湿弁３０に至る前までの区間、または暖房運転で除湿弁３０の後から冷媒出口までの区間で、風上側から１列目の伝熱管２０Ａは、伝熱管２０Ａの溝部２１ａの面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）が０．００７５（ｍｍ２／ｍｍ）から０．０１２５（ｍｍ２／ｍｍ）の範囲となるように形成されている。また、風上側から２列目以降の伝熱管２０Ｂは、伝熱管２０Ｂの溝部２１ｂの面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）が０．００２８（ｍｍ２／ｍｍ）から０．００７４（ｍｍ２／ｍｍ）の範囲となるように形成されている。 In the heat exchange device 1 according to the first embodiment, in the section from the refrigerant inlet to the dehumidifying valve 30 in the cooling operation, or in the section from the rear of the dehumidifying valve 30 to the refrigerant outlet in the heating operation, one row from the windward side In the heat transfer tube 20A of the eye, 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. In the heat transfer tubes 20B in the second and subsequent rows from the windward side, 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).
　このように、熱交換装置１において、風上側から１列目の伝熱管２０Ａの溝部２１ａの面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）を０．００７５（ｍｍ２／ｍｍ）から０．０１２５（ｍｍ２／ｍｍ）の範囲に設定したのは、１列目の伝熱管２０Ａの溝部２１ａの面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）を０．００７５（ｍｍ２／ｍｍ）より小さくすると、溝部２１ａに保持される液冷媒が少なくなり、山部２２ａへの液膜厚さが厚くなり、管内伝熱性能が全体で見ると低下するからである。また、１列目の伝熱管２０Ａの溝部２１ａの面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）を０．０１２５（ｍｍ２／ｍｍ）より大きくすると、液冷媒保持効果が低下し、管内伝熱性能が全体で見ると低下するからである。風上側から１列目の伝熱管２０Ａの溝部２１ａの面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）を前述の範囲とすることで、図３のように１列目の伝熱管２０Ａ内の溝部２１ａの毛細管作用に伴う液冷媒保持効果を利用して、管内伝熱性能を向上させることができる。 Thus, in the heat exchanger 1, 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 This is because the liquid refrigerant held in the groove portion 21a decreases, the liquid film thickness to the peak portion 22a increases, and the in-tube heat transfer performance decreases as a whole. Further, if 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. By setting the ratio (Aa / Do) of the area Aa and the outer diameter Do of the groove portion 21a of the first row of heat transfer tubes 20A from the windward side to the above range, the inside of the first row of heat transfer tubes 20A as shown in FIG. The heat transfer performance in the tube can be improved by utilizing the liquid refrigerant holding effect accompanying the capillary action of the groove portion 21a.
　また、熱交換装置１において、風上側から２列目の伝熱管２０Ｂの溝部２１ｂの面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）を０．００２８（ｍｍ２／ｍｍ）から０．００７４（ｍｍ２／ｍｍ）の範囲に設定したのは、風上側から２列目の伝熱管２０Ｂの溝部２１ｂの面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）を０．００２８（ｍｍ２／ｍｍ）より小さくすると、溝部２１ｂに保持される液冷媒が少なくなり、山部２２ｂへの液膜厚さが厚くなり、管内伝熱性能が全体で見ると低下するからである。また、風上側から２列目の伝熱管２０Ｂの溝部２１ｂの面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）を０．００７４（ｍｍ２／ｍｍ）より大きくすると、液冷媒保持効果が低下し、管内伝熱性能が全体で見ると低下するからである。風上側から２列目の伝熱管２０Ｂの溝部２１ｂの面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）を前述の範囲とすることで、１列目の伝熱管２０Ａと同様に隣り合う溝部２１ｂの毛細管作用に伴う液冷媒４０の保持効果を利用して、管内伝熱性能を向上させることができる。 In the heat exchange device 1, 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. Moreover, if 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. By setting the ratio (Ab / Do) of the area Ab and the outer diameter Do of the groove portion 21b of the second row of heat transfer tubes 20B from the windward side to the above range, adjacent groove portions as in the first row of heat transfer tubes 20A. The heat transfer performance in the tube can be improved by utilizing the retention effect of the liquid refrigerant 40 accompanying the capillary action of 21b.
　以上のように、本実施の形態１の熱交換装置１によれば、複数の伝熱管２０を複数のフィン１０に挿通させてなる２列以上の室内側熱交換器において、冷房運転で冷媒入口から除湿弁３０に至る前までの区間、または暖房運転で除湿弁３０の後から冷媒出口までの区間で、風上側から１列目の伝熱管２０Ａの溝部２１ａの面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）が、風上側から２列目以降の伝熱管２０Ｂの溝部２１ｂの面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）より大きく形成されているので、管内伝熱性能を向上させることができ、熱交換率（伝熱管通過前後の熱量の比率）を高くすることができる。そのため、省エネルギ化を図ることができる。また、冷媒回路内の冷媒の減量、効率を維持しつつ、小型化を図ることもできる。 As described above, according to 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.
　以下、実施例について、本発明の範囲から外れる比較例と比較して説明する。表１に示すように、１列目の伝熱管２０Ａの溝部２１ａの面積Ａａ／外径Ｄｏが０．００７５、０．００９５、０．０１１５、０．０１２５（ｍｍ２／ｍｍ）、２列目の伝熱管２０Ｂの溝部２１ｂの面積Ａｂ／外径Ｄｏが０．００３５（ｍｍ２／ｍｍ）である実施例１～４の熱交換装置１を作製した（実施例１～４）。また、比較例として、１列目の伝熱管２０Ａの溝部２１ａの面積Ａａ／外径Ｄｏが０．００５、０．０３５（ｍｍ２／ｍｍ）、２列目の伝熱管２０Ｂの溝部２１ｂの面積Ａｂ／外径Ｄｏが０．００３５（ｍｍ２／ｍｍ）である熱交換装置を作製した（比較例１，２）。 Hereinafter, examples will be described in comparison with comparative examples that are out of the scope of the present invention. As shown in Table 1, 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). As a comparative example, 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).
Figure JPOXMLDOC01-appb-T000001
Figure JPOXMLDOC01-appb-T000001
　表１から明らかなように、実施例１～４の熱交換装置１は、いずれも比較例１，２の熱交換器と比べて熱交換率が高く、管内伝熱性能が向上していた。 As is clear from Table 1, 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.
　表２に示すように、１列目の伝熱管２０Ａの溝部２１ａの面積Ａａ／外径Ｄｏが０．００９５（ｍｍ２／ｍｍ）、２列目の伝熱管２０Ｂの溝部２１ｂの面積Ａｂ／外径Ｄｏが０．００２８、０．００３５、０．００５、０．００７４（ｍｍ２／ｍｍ）である実施例５～８の熱交換装置１を作製した。また、比較例として、１列目の伝熱管２０Ａの溝部２１ａの面積Ａａ／外径Ｄｏが０．００９５（ｍｍ２／ｍｍ）、２列目の伝熱管２０Ｂの溝部２１ｂの面積Ａｂ／外径Ｄｏが０．００２５、０．００８（ｍｍ２／ｍｍ）である熱交換装置を作製した（比較例３，４）。 As shown in Table 2, 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. Further, as a comparative example, 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).
Figure JPOXMLDOC01-appb-T000002
Figure JPOXMLDOC01-appb-T000002
　表２から明らかなように、実施例５～８の熱交換装置１は、いずれも比較例３，４の熱交換器と比べて熱交換率が高く、管内伝熱性能が向上していた。 As is clear from Table 2, the heat exchange devices 1 of Examples 5 to 8 all had a higher heat exchange rate than the heat exchangers of Comparative Examples 3 and 4, and the heat transfer performance in the tube was improved.
　なお、主熱交換器１Ａと副熱交換器１Ｂを、いずれも複数列で構成される熱交換器の群で構成したもの、つまりフィン１０が気体の流れ方向に複数列に分割されているものを例に挙げて説明したが、これに限るものではない。例えば、フィン１０を気体の流れ方向で分割せず、これに伝熱管を気体の流れ方向に複数列挿通させる構成としてもよい。 Note that 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. However, the present invention is not limited to this. For example, it is good also as a structure which does not divide | segment the fin 10 in the gas flow direction, and makes this arrange | position a heat exchanger tube in multiple rows in the gas flow direction.
実施の形態２.
　図４は本発明の実施形態２に係る空気調和機の冷媒回路図を示すもので、前述の実施の形態１で説明した熱交換装置を室内熱交換器として用いたものである。
　本実施の形態２の空気調和機は、圧縮機６１、四方弁６２、室外熱交換器６３、減圧器６４、及び室内熱交換器６５が、冷媒配管７０によって閉ループ状に接続され、室内機５０と室外機６０との間にガスバルブ６８と液バルブ６９が配置されている。また、室外熱交換器６３には室外送風機６６が併設され、室内熱交換器６５には室内送風機６７が併設されている。 Embodiment 2.
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.
In the air conditioner of the second embodiment, 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, and the indoor heat exchanger 65 is provided with an indoor fan 67.
　本実施の形態２の空気調和機において、冷房運転時には低圧低温のガス冷媒は室外機６０の圧縮機６１により高温高圧のガス冷媒に圧縮され、四方弁６２に送られる。そして、四方弁６２から冷媒配管７０により室外熱交換器６３に導かれてガス冷媒が液化し、凝縮熱を室外に放出する（室外熱交換器６３が凝縮器として作用する）。室外熱交換器６３から出た高圧の液冷媒は、減圧器６４により低圧低温の気液二相冷媒となり、液バルブ６９を介して室内機５０の室内熱交換器６５に導かれる。ここで、室内の空気中の熱を吸収して冷媒が蒸発し、低圧低温のガス冷媒となり、冷房運転を行う（室内熱交換器６５が蒸発器として作用する）。そして、低圧低温のガス冷媒は、ガスバルブ６８、四方弁６２を経て圧縮機６１に導かれ、冷媒サイクル運転を行う。 In the air conditioner of the second embodiment, during the cooling operation, 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 | induces to the outdoor heat exchanger 63 by the refrigerant | coolant piping 70 from the four-way valve 62, a gas refrigerant liquefies, and discharge | releases condensation heat outside (the outdoor heat exchanger 63 acts as a condenser). 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. Here, 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.
　暖房運転を行う場合は、四方弁６２を切り換えて冷媒の流れを冷房運転の場合と逆方向にすることにより、室内熱交換器６５が凝縮機、室外熱交換器６３が蒸発器として作用する。それ以外は冷房運転の場合と同様である。 When performing the heating 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.
　本実施の形態２によれば、室内熱交換器６５として前述の実施の形態１の熱交換装置１を用いているので、室内熱交換器６５の管内伝熱性能を向上させることができ、熱交換率（伝熱管通過前後の熱量の比率）を高くすることができる。そのため、省エネルギ化を図ることができる。また、室内熱交換器６５の冷媒回路内の冷媒の減量、効率を維持しつつ、小型化を図ることもできる。 According to the second embodiment, since 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) can be increased. Therefore, energy saving can be achieved. Further, it is possible to reduce the size of the indoor heat exchanger 65 while reducing the amount of refrigerant in the refrigerant circuit and maintaining the efficiency.
　なお、前述した実施の形態１，２では、本発明に係る熱交換装置に関し、冷凍装置または空気調和装置への適用について説明したが、本発明はこれらの装置に限定されるものではない。例えば、本発明は、ヒートポンプ装置のように、冷媒回路を構成し、蒸発器、凝縮器となる熱交換器を有する他の冷凍サイクル装置にも適用することができる。 In the first and second embodiments, 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. However, the present invention is not limited to these apparatuses. For example, 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.
　１　熱交換装置、１Ａ　主熱交換器、１Ｂ　副熱交換器、１０　フィン、２０　伝熱管、２０Ａ　１列目の伝熱管（第１伝熱管）、２０Ｂ　２列目以降の伝熱管（第２伝熱管）、２１ａ、２１ｂ　溝部、２２ａ，２２ｂ　山部、３０　除湿弁、４０　液冷媒、５０　室内機、６０　室外機、６１　圧縮機、６２　四方弁、６３　室外熱交換器、６４　減圧器、６５　室内熱交換器、６６　室外送風機、６７　室内送風機、６８　ガスバルブ、６９　液バルブ、７０　冷媒配管、Ａａ　１列目の伝熱管の管軸に直交する平面における溝部の面積、Ａｂ　２列目以降の伝熱管の管軸に直交する平面における溝部の面積、Ｄｏ　外径、Ｐａ　１列目の伝熱管の溝部の溝ピッチ、Ｐｂ　２列目の伝熱管の溝部の溝ピッチ。 1 Heat Exchanger, 1A Main Heat Exchanger, 1B Sub Heat Exchanger, 10 Fins, 20 Heat Transfer Tube, 20A 1st Row Heat Transfer Tube (1st Heat Transfer Tube), 20B 2nd Row Heat Transfer Tube (2nd Transfer Tube) Heat pipe), 21a, 21b groove, 22a, 22b mountain, 30 dehumidification valve, 40 liquid refrigerant, 50 indoor unit, 60 outdoor unit, 61 compressor, 62 four-way valve, 63 outdoor heat exchanger, 64 decompressor, 65 indoor Heat exchanger, 66 outdoor blower, 67 indoor blower, 68 gas valve, 69 liquid valve, 70 refrigerant pipe, Aa, groove area in the plane perpendicular to the tube axis of the first row heat transfer tube, Ab second row and subsequent heat transfer tubes The groove area on the plane perpendicular to the tube axis, Do outer diameter, Pa groove pitch of the first heat transfer tube groove, and Pb groove pitch of the second heat transfer tube groove.

Claims (5)

  1. 　気体の流れに対して上流側に配置された第１伝熱管と、前記第１伝熱管よりも下流側に前記第１伝熱管と並んで配置された第２伝熱管とを少なくとも有する熱交換装置において、
    　前記第１伝熱管及び前記第２伝熱管は管内面に溝を有し、
    　前記第１伝熱管は、管軸に直交する平面における溝部の面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）が、前記第２伝熱管の管軸に直交する平面における溝部の面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）より大きく形成された熱交換装置。     A heat exchange device having at least a first heat transfer tube disposed on the upstream side with respect to a gas flow and a second heat transfer tube disposed on the downstream side of the first heat transfer tube alongside the first heat transfer tube. In
    The first heat transfer tube and the second heat transfer tube have grooves on the inner surface of the tube,
    In the first heat transfer tube, the ratio (Aa / Do) of the groove area Aa to the outer diameter Do in the plane orthogonal to the tube axis is the groove area Ab in the plane orthogonal to the tube axis of the second heat transfer tube. A heat exchange device formed larger than the ratio (Ab / Do) to the outer diameter Do.
  2. 　前記熱交換装置は複数の熱交換器を備え、前記複数の熱交換器の間が除湿弁を介して接続されており、
    　冷房運転で冷媒入口から前記除湿弁の前までの区間、または暖房運転で前記除湿弁の後から冷媒出口までの区間で、前記第１伝熱管の管軸に直交する平面における溝部の面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）は、前記第２伝熱管の管軸に直交する平面における溝部の面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）より大きく形成された請求項１記載の熱交換装置。     The heat exchange device includes a plurality of heat exchangers, and the plurality of heat exchangers are connected via dehumidification valves,
    In the section from the refrigerant inlet to the front of the dehumidification valve in the cooling operation, or the section from the rear of the dehumidification valve to the refrigerant outlet in the heating operation, the groove area Aa in a plane orthogonal to the tube axis of the first heat transfer tube; The ratio (Aa / Do) with the outer diameter Do is formed to be 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 heat exchange apparatus as described.
  3. 　前記第１伝熱管の管軸に直交する平面における溝部の面積Ａａと外径Ｄｏとの比（Ａａ／Ｄｏ）は０．００７５（ｍｍ２／ｍｍ）から０．０１２５（ｍｍ２／ｍｍ）の範囲、前記第２伝熱管の管軸に直交する平面における溝部の面積Ａｂと外径Ｄｏとの比（Ａｂ／Ｄｏ）は０．００２８（ｍｍ２／ｍｍ）から０．００７４（ｍｍ２／ｍｍ）の範囲で形成された請求項１又は２記載の熱交換装置。 The ratio (Aa / Do) of the groove area Aa to the outer diameter Do in the plane orthogonal to the tube axis of the first heat transfer tube is 0.0075 (mm 2 / mm) to 0.0125 (mm 2 / mm). The ratio (Ab / Do) of the area Ab and the outer diameter Do of the groove portion in a plane perpendicular to the tube axis of the second heat transfer tube is from 0.0028 (mm 2 / mm) to 0.0074 (mm 2 / mm) The heat exchange device according to claim 1 or 2 formed in a range of
  4. 　前記第１伝熱管及び前記第１伝熱管の前記溝部の溝高さは変えずに、前記第１伝熱管の前記溝部の溝ピッチを、前記第２伝熱管の前記溝部の溝ピッチより大きくすることで、前記第１伝熱管の前記比（Ａａ／Ｄｏ）が前記第２伝熱管の前記比（Ａｂ／Ｄｏ）より大きく形成された請求項１～３のいずれか一項に記載の熱交換装置。 The groove pitch of the groove portion of the first heat transfer tube is made larger than the groove pitch of the groove portion of the second heat transfer tube without changing the groove height of the groove portion of the first heat transfer tube and the first heat transfer tube. The heat exchange according to any one of claims 1 to 3, wherein the ratio (Aa / Do) of the first heat transfer tube is larger than the ratio (Ab / Do) of the second heat transfer tube. apparatus.
  5. 　少なくとも圧縮機、凝縮器、減圧器、及び蒸発器を有し、これらが冷媒配管によって閉ループ状に接続された冷凍サイクル装置であって、
    　前記凝縮器又は前記蒸発器として請求項１～４のいずれか一項に記載の熱交換装置を用いた冷凍サイクル装置。     A refrigeration cycle apparatus having at least a compressor, a condenser, a decompressor, and an evaporator, which are connected in a closed loop by a refrigerant pipe,
    A refrigeration cycle apparatus using the heat exchange device according to any one of claims 1 to 4 as the condenser or the evaporator.
PCT/JP2014/052790 2013-02-14 2014-02-06 Heat exchange device and refrigeration cycle device equipped with same WO2014125997A1 (en)

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JP7403742B2 (en) 2015-12-29 2023-12-25 ズターコア エルティーディー． Vacuum-based thermal management system
MY182106A (en) * 2016-11-28 2021-01-18 Mitsubishi Electric Corp Heat exchanger, refrigeration cycle apparatus, and method for manufacturing heat exchanger
DE112019007149T5 (en) * 2019-04-03 2021-12-23 Mitsubishi Electric Corporation Heat exchanger and air conditioning

Citations (3)

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Publication number Priority date Publication date Assignee Title
JP2000329486A (en) * 1999-05-17 2000-11-30 Matsushita Electric Ind Co Ltd Finned heat exchanger
JP2005083715A (en) * 2003-09-11 2005-03-31 Sharp Corp Heat exchanger
JP2009127882A (en) * 2007-11-20 2009-06-11 Mitsubishi Electric Corp Heat exchanger, indoor unit, and air conditioner

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JPH11257800A (en) * 1998-03-09 1999-09-24 Sanyo Electric Co Ltd Heat exchanger and air conditioner with exchanger
JP5197820B2 (en) * 2011-09-12 2013-05-15 三菱電機株式会社 Refrigeration cycle equipment

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000329486A (en) * 1999-05-17 2000-11-30 Matsushita Electric Ind Co Ltd Finned heat exchanger
JP2005083715A (en) * 2003-09-11 2005-03-31 Sharp Corp Heat exchanger
JP2009127882A (en) * 2007-11-20 2009-06-11 Mitsubishi Electric Corp Heat exchanger, indoor unit, and air conditioner

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