JP2008267779A - Heat transfer tube - Google Patents

Heat transfer tube Download PDF

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JP2008267779A
JP2008267779A JP2007272380A JP2007272380A JP2008267779A JP 2008267779 A JP2008267779 A JP 2008267779A JP 2007272380 A JP2007272380 A JP 2007272380A JP 2007272380 A JP2007272380 A JP 2007272380A JP 2008267779 A JP2008267779 A JP 2008267779A
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heat transfer
transfer tube
fin
tube
fins
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JP5006155B2 (en
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Yasutoshi Mori
康敏 森
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Furukawa Electric Co Ltd
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Furukawa Electric Co Ltd
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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

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  • Engineering & Computer Science (AREA)
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  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Metal Extraction Processes (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat transfer tube composed of an aluminum material having sufficient compression strength, and internal-face groove processing can be favorably performed. <P>SOLUTION: This heat transfer tube provided with fins on the tube inner face composed of a JISA3000 system (Al-Mn system) aluminum alloy, has a ratio [D/t] of an outer diameter D and a bottom thickness t of the heat transfer tube of 10.0 or larger and 17.5 or smaller, and a bottom width W of the fin is 0.1 mm or larger. An apex angle α of the fins 2 formed on the inner face of the heat transfer tube 1 is 18 degrees or smaller, or a lead angle β is 20 degrees or larger. Since shapes of the fins 2 (groove 3) of the inner face satisfy prescribed conditions in the heat transfer tube 1, a groove can be favorably formed on the inner face even if the bottom thickness is increased to have sufficient compression strength. Further weight can be reduced since the heat transfer tube is composed of the aluminum material. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は冷凍機や空調機等の熱交換器に用いられる伝熱管に関するものである。   The present invention relates to a heat transfer tube used in a heat exchanger such as a refrigerator or an air conditioner.

一般に空調機や冷凍機の熱交換器に用いられる伝熱管は、管内に冷媒としてフロン等を流して熱交換を行わせるもので、最近では管内面に断面形状が三角形や台形のフィンを持つ伝熱管（内面溝付管）を使用することによって熱交換器の高効率化や省エネルギー化が進められている。これらの伝熱管は、一般に、転造加工により製造される。   In general, heat transfer tubes used in heat exchangers for air conditioners and refrigerators exchange heat by flowing chlorofluorocarbon or other refrigerant as a refrigerant in the tubes. Recently, the heat transfer tubes have triangular or trapezoidal fins on the inner surface. The use of heat pipes (inner grooved pipes) has promoted higher efficiency and energy saving of heat exchangers. These heat transfer tubes are generally manufactured by a rolling process.

空調機用熱交換器に対しては高性能化、小型軽量化の要求が強く、またヒートポンプ式エアコンの普及により同一の伝熱管で蒸発性能と凝縮性能の両性能をともに向上させた伝熱管が必要とされている。このような要求に応えるべく、フィン間の溝の深さ、溝のリード角、底肉厚、溝の形状等を規定した伝熱管が提案されている（特許文献１）。   There is a strong demand for higher performance, smaller size and lighter weight for heat exchangers for air conditioners, and heat transfer tubes that have improved both evaporation performance and condensation performance with the same heat transfer tube due to the widespread use of heat pump air conditioners. is needed. In order to meet such demands, a heat transfer tube that defines the groove depth between fins, groove lead angle, bottom wall thickness, groove shape, and the like has been proposed (Patent Document 1).

一方、前記伝熱管にはこれまで主に銅や銅合金等の銅系材料が使用されてきたが、空調機用熱交換器の小型軽量化の要求に対応するため、アルミニウムやアルミニウム合金等のアルミ系材料を使用することが検討されている（特許文献２）。   On the other hand, copper-based materials such as copper and copper alloys have been mainly used so far for the heat transfer tubes. However, in order to meet the demand for smaller and lighter heat exchangers for air conditioners, aluminum and aluminum alloys are used. The use of aluminum-based materials has been studied (Patent Document 2).

特開２００３−２８７３８３号公報JP 2003-287383 A 特開２００１−２８９５８５号公報JP 2001-289585 A

しかしながら、銅系材料の伝熱管で採用していた内面の溝（フィン）形状を、そのままアルミ系材料の伝熱管に用いると伝熱管の耐圧強度基準を満足することができず、熱交換器に使用できないという問題が生じた。これはアルミ系材料の強度が低いことが原因なので、対策としては伝熱管の底肉厚を厚くすることが考えられるが、そうすると内面のフィン（溝）の加工が困難になり、場合によっては、フィンが加工中に千切れてしまうといった問題が発生した。
本発明は、十分な耐圧強度を有し、かつ内面溝加工が良好に行えるアルミ系材料からなる伝熱管の提供を目的とする。 However, if the inner groove (fin) shape used in copper-based heat transfer tubes is used as is in aluminum-based heat transfer tubes, the pressure resistance strength standard of the heat transfer tubes cannot be satisfied, and the heat exchanger There was a problem that it could not be used. Since this is due to the low strength of the aluminum-based material, it is conceivable to increase the bottom wall thickness of the heat transfer tube as a countermeasure, but doing so makes it difficult to process the fins (grooves) on the inner surface, There was a problem that the fins were broken during processing.
An object of this invention is to provide the heat exchanger tube which consists of an aluminum-type material which has sufficient pressure-resistant intensity | strength and can perform internal surface groove processing satisfactorily.

請求項１に記載の発明は、ＪＩＳＡ３０００系（Ａｌ−Ｍｎ系）アルミニウム合金からなる管内面にフィンが形成された伝熱管であって、前記伝熱管の外径（Ｄ）と底肉厚（ｔ）の比［Ｄ／ｔ］が１０．０以上、１７．５以下であり、かつ前記フィン底幅Ｗが０．１ｍｍ以上であることを特徴とする伝熱管である。   The invention according to claim 1 is a heat transfer tube in which fins are formed on the inner surface of a tube made of a JIS A3000 (Al-Mn) aluminum alloy, the outer diameter (D) of the heat transfer tube and the bottom wall thickness (t ) Ratio [D / t] is 10.0 or more and 17.5 or less, and the fin bottom width W is 0.1 mm or more.

請求項２に記載の発明は、請求項１に記載の伝熱管において、前記伝熱管の内面に形成されたフィンの頂角αが１８度以下であることを特徴とする伝熱管である。   The invention according to claim 2 is the heat transfer tube according to claim 1, wherein the apex angle α of the fin formed on the inner surface of the heat transfer tube is 18 degrees or less.

請求項３に記載の発明は、請求項１または２に記載の伝熱管において、前記伝熱管の内面に形成されたフィンのリード角βが２０度以上であることを特徴とする伝熱管である。   The invention according to claim 3 is the heat transfer tube according to claim 1 or 2, wherein the lead angle β of the fin formed on the inner surface of the heat transfer tube is 20 degrees or more. .

本発明の伝熱管は、ＪＩＳＡ３０００系（Ａｌ−Ｍｎ系）アルミニウム合金からなる管内面にフィンが形成された伝熱管であって、その外径（Ｄ）と底肉厚（ｔ）の比［Ｄ／ｔ］を１０．０以上、１７．５以下に規定し、さらに前記フィン底幅Ｗを０．１ｍｍ以上に適正に規定したものなので、十分な耐圧強度を付与するために底肉厚を厚くしても、内面の溝加工を良好に行うことができる。従って溝形状および耐圧強度に優れる。さらに前記フィンの頂角αを１８度以下とし、或いは前記フィンのリード角βを２０度以上とすることにより伝熱特性が向上する。しかも本発明の伝熱管はアルミ系材料からなるため軽量である。よって産業上顕著な効果を奏する。   The heat transfer tube of the present invention is a heat transfer tube in which fins are formed on the inner surface of a tube made of a JIS A3000 (Al-Mn) aluminum alloy, and the ratio of the outer diameter (D) to the bottom wall thickness (t) [D / T] is specified to be 10.0 or more and 17.5 or less, and the fin bottom width W is appropriately specified to be 0.1 mm or more, so that the bottom wall thickness is increased in order to provide sufficient pressure strength. Even so, the groove processing of the inner surface can be performed satisfactorily. Accordingly, the groove shape and pressure strength are excellent. Furthermore, the heat transfer characteristic is improved by setting the apex angle α of the fin to 18 degrees or less or the lead angle β of the fin to 20 degrees or more. Moreover, the heat transfer tube of the present invention is lightweight because it is made of an aluminum-based material. Therefore, there is a significant industrial effect.

本発明の伝熱管を構成するＪＩＳＡ３０００系（Ａｌ−Ｍｎ系）アルミニウム合金は、溝付加工時におけるメタルフローが良好でフィンが高品質に形成される。さらにフィン成形時に外表面に発生し易いまくれ込みなどの欠陥が生じ難い。中でもＪＩＳＡ３００３およびＪＩＳＡ３００４はメタルフローが特に良好で推奨される。   The JISA 3000 series (Al-Mn series) aluminum alloy constituting the heat transfer tube of the present invention has a good metal flow at the time of grooving and fins are formed with high quality. Furthermore, defects such as curling up that are likely to occur on the outer surface during fin molding are unlikely to occur. Among them, JISA3003 and JISA3004 have a particularly good metal flow and are recommended.

本発明において、伝熱管の外径Ｄ（図１（イ）参照）と底肉厚ｔ（図１（ハ）参照）の比［Ｄ／ｔ］を１０．０以上、１７．５以下に規定する理由は、１０．０未満では伝熱管の外径Ｄに対して底肉厚ｔが厚くなり、その結果、溝付加工時に材料が長さ方向に伸び易くなってフィン部へのメタルフローが悪化し、１７．５を超えると管の外径Ｄに対して底肉厚ｔが薄くなって耐圧強度が低下するためである。メタルフローが悪化すると表面欠陥が発生し、極端に悪化するとフィンが千切れることもある。比［Ｄ／ｔ］の好ましい範囲は１２．１以上、１７．５以下、より好ましくは１３．０以上、１７．５以下である。   In the present invention, the ratio [D / t] between the outer diameter D of the heat transfer tube (see FIG. 1 (a)) and the bottom wall thickness t (see FIG. 1 (c)) is defined as 10.0 or more and 17.5 or less. The reason for this is that if the thickness is less than 10.0, the bottom wall thickness t becomes thicker than the outer diameter D of the heat transfer tube, and as a result, the material tends to extend in the length direction during grooving and the metal flow to the fin portion This is because when the pressure exceeds 17.5, the bottom wall thickness t becomes smaller than the outer diameter D of the tube, and the pressure resistance is lowered. When the metal flow deteriorates, surface defects occur, and when the metal flow deteriorates extremely, the fins may be broken. A preferable range of the ratio [D / t] is 12.1 or more and 17.5 or less, more preferably 13.0 or more and 17.5 or less.

本発明において、フィンの底幅Ｗを０．１ｍｍ以上に規定する理由は、０．１ｍｍ未満ではメタルフローが悪化して溝付加工性が低下するためである。フィンの底幅Ｗは大きいほど溝加工性は向上するが０．４ｍｍを超えるとその効果が飽和する。フィン底幅Ｗの好ましい範囲は０．１２〜０．３ｍｍである。ここでフィンの底幅Ｗはフィンの長さ方向に垂直な断面における底幅のことをいう（図１（ロ）、（ハ）参照）。   In the present invention, the reason why the bottom width W of the fin is defined to be 0.1 mm or more is that if it is less than 0.1 mm, the metal flow is deteriorated and the grooving workability is lowered. Groove workability is improved as the bottom width W of the fin is increased, but the effect is saturated when the fin width exceeds 0.4 mm. A preferable range of the fin bottom width W is 0.12 to 0.3 mm. Here, the bottom width W of the fin refers to the bottom width in a cross section perpendicular to the length direction of the fin (see FIGS. 1B and 1C).

本発明において、伝熱管内面のフィンの頂角αを１８度以下に規定することにより伝熱特性が向上する。フィンの頂角αは小さい程良いが、５度未満ではその効果が飽和する。フィンの頂角αの好ましい範囲は１１度以上１６度以下である。ここでフィンの頂角αはフィンの長さ方向に垂直な断面におけるフィンの頂角のことをいう（図１（ハ）参照）。   In the present invention, the heat transfer characteristics are improved by defining the apex angle α of the fin on the inner surface of the heat transfer tube to 18 degrees or less. The smaller the apex angle α of the fin, the better. However, if the angle is less than 5 degrees, the effect is saturated. A preferable range of the apex angle α of the fin is 11 degrees or more and 16 degrees or less. Here, the apex angle α of the fin refers to the apex angle of the fin in a cross section perpendicular to the length direction of the fin (see FIG. 1C).

本発明において、管内面のフィン（溝）のリード角β（リード角β:伝熱管の長さ方向とフィンの長さ方向とのなす角度、図１（ロ）参照）を２０度以上に規定することにより伝熱特性が向上する。リード角βは大きい程良いが、６０度以上ではその効果が飽和する。リード角βの好ましい範囲は２５度以上５５度以下である。   In the present invention, the lead angle β of the fin (groove) on the inner surface of the tube (lead angle β: angle formed between the length direction of the heat transfer tube and the length direction of the fin, see FIG. 1B) is specified to be 20 degrees or more. This improves the heat transfer characteristics. A larger lead angle β is better, but the effect is saturated at 60 ° or more. A preferable range of the lead angle β is 25 degrees or more and 55 degrees or less.

本発明において、伝熱管内面の各フィンの側面形状は、フィン相互間の溝に向かって一様に傾斜するフラットな斜面、円弧状の凸状斜面など任意であるが、円弧状或いは多角形状の凹状斜面は冷媒がフィン上に滞留し易く好ましい。   In the present invention, the shape of the side surface of each fin on the inner surface of the heat transfer tube is arbitrary, such as a flat slope or an arcuate convex slope that uniformly inclines toward the groove between the fins. The concave slope is preferable because the refrigerant tends to stay on the fins.

以下に、本発明を実施例に基づきさらに詳細に説明するが、本発明はこれに限定されるものではない。   Hereinafter, the present invention will be described in more detail based on examples, but the present invention is not limited thereto.

［実施例１］
ＪＩＳＡ３００３系アルミニウム合金からなる素管を転造加工して伝熱管（内面螺旋溝付管）を製造した。前記伝熱管は、外径Ｄが７．００ｍｍ、フィン底幅Ｗが０．１８ｍｍ、溝のリード角βが２８度、フィン（隆起部）の数が４８、フィンの高さＨが０．２２ｍｍ、フィン頂角αが１５度である。底肉厚ｔは０．４０〜０．７０ｍｍの範囲で種々に変化させた。フィンの側面形状は円弧状凹状斜面とした。 [Example 1]
A base pipe made of a JISA3003 series aluminum alloy was rolled to produce a heat transfer pipe (inner spiral grooved pipe). The heat transfer tube has an outer diameter D of 7.00 mm, a fin bottom width W of 0.18 mm, a groove lead angle β of 28 degrees, a number of fins (protrusions) of 48, and a fin height H of 0.22 mm. The fin apex angle α is 15 degrees. The bottom wall thickness t was variously changed in the range of 0.40 to 0.70 mm. The side surface shape of the fin was an arcuate concave slope.

得られた伝熱管について、管内面の溝（フィン）形状、耐圧強度、伝熱特性を調べた。
前記溝形状は、伝熱管（長さ３００ｍｍ）を縦に２分割して管内面のフィンの高さ、底肉厚、底幅などを測定して調べた。前記測定値が基準値を満足し、かつ肉眼観察で皺などの欠陥が全く認められないものは溝形状が極めて良好（◎）、実用上問題ない程度の浅い皺が極少数認められる以外は欠陥が存在しないものは良好（○）、実用上問題ない程度の浅い皺が少数認められる以外は欠陥が存在しないものは略良好（□）、管内面のフィンの寸法が基準値を外れたり、フィン或いは溝に深い皺や亀裂が存在したり、フィンが破断したり、千切れたりしたものは不良（×）と評価した。 The obtained heat transfer tube was examined for the groove (fin) shape, pressure strength, and heat transfer characteristics of the tube inner surface.
The groove shape was examined by measuring the height, bottom thickness, bottom width, etc. of the fins on the inner surface of the heat transfer tube (length: 300 mm) divided into two vertically. If the measured value satisfies the reference value and no defects such as wrinkles are observed by visual observation, the groove shape is very good (◎), and there are only a few defects that are shallow enough to be practically acceptable. If there is no defect, it is good (○), and there are few defects that are not problematic in practice, except that there are few defects, it is almost good (□). Alternatively, a case where a deep flaw or crack was present in the groove, or the fin was broken or broken was evaluated as defective (x).

前記耐圧強度は、伝熱管（長さ３００ｍｍ）の一方の開口部を閉塞し、他方の開口部から伝熱管内部に水を入れ、水圧発生器にて水圧を除々に上昇させ、伝熱管が破裂したときの水圧を測定した。各５本ずつ測定し、その平均値が基準値の１２．４５ＭＰａ（設計圧力の３倍）以上のものは耐圧強度が優れる（○）、基準値未満のものは劣る（×）と評価した。   The pressure resistance is such that one opening of a heat transfer tube (length: 300 mm) is closed, water is poured into the heat transfer tube from the other opening, the water pressure is gradually increased by a water pressure generator, and the heat transfer tube bursts. The water pressure was measured. Five samples were measured, and the average value of 12.45 MPa (three times the design pressure) or higher of the reference value was evaluated as excellent in pressure resistance (◯), and the average value of less than the reference value was evaluated as poor (×).

前記伝熱特性は従来公知の伝熱性能試験装置（図２（イ）、（ロ）参照）を用いて、管内熱伝達率（管内凝縮および管内蒸発）を測定して調べた。冷媒質量速度は２５０ｋｇ／ｍ２・ｓとした。その他の試験条件は表１に示した。従来の銅製内面溝付伝熱管についても管内熱伝達率を上記と同じ方法で測定した。管内熱伝達率は各伝熱管３本について測定し、その平均値をその伝熱管の管内熱伝達率とした。 The heat transfer characteristics were examined by measuring the heat transfer coefficient in the tube (condensation in the tube and evaporation in the tube) using a conventionally known heat transfer performance test apparatus (see FIGS. 2A and 2B). The refrigerant mass rate was 250 kg / m 2 · s. Other test conditions are shown in Table 1. The heat transfer coefficient in the tube of the conventional copper inner grooved heat transfer tube was also measured by the same method as described above. The heat transfer coefficient in the tube was measured for each of the three heat transfer tubes, and the average value was defined as the heat transfer coefficient in the tube of the heat transfer tube.

Figure 2008267779
Figure 2008267779

［実施例２］
フィンの頂角αを２０度または／およびフィンのリード角βを１８度とした他は実施例１と同じ形状（寸法）の伝熱管を製造し、実施例１と同じ調査を行った。 [Example 2]
A heat transfer tube having the same shape (dimension) as in Example 1 was manufactured except that the apex angle α of the fin was 20 degrees and / or the lead angle β of the fin was 18 degrees, and the same investigation as in Example 1 was performed.

［比較例１］
底肉厚ｔを０．８０ｍｍまたは０．３９ｍｍとした他は、実施例１と同じ形状（寸法）の伝熱管を製造し、実施例１と同じ調査を行った。 [Comparative Example 1]
A heat transfer tube having the same shape (dimension) as in Example 1 was manufactured except that the bottom wall thickness t was set to 0.80 mm or 0.39 mm, and the same investigation as in Example 1 was performed.

［比較例２］
フィン底幅Ｗを０．０８ｍｍとした他は、実施例１と同じ形状（寸法）の伝熱管を製造し、実施例１と同じ調査を行った。 [Comparative Example 2]
A heat transfer tube having the same shape (dimension) as in Example 1 was manufactured except that the fin bottom width W was 0.08 mm, and the same investigation as in Example 1 was performed.

実施例１、２、比較例１、２の調査結果を表２に示した。伝熱特性は実施例１と同じ方法で測定した銅製内面溝付伝熱管の管内熱伝達率（ｎ＝３の平均値）を１００としたときの比で示した。   The investigation results of Examples 1 and 2 and Comparative Examples 1 and 2 are shown in Table 2. The heat transfer characteristics are shown as a ratio when the in-tube heat transfer coefficient (average value of n = 3) of the copper internally grooved heat transfer tube measured by the same method as in Example 1 is 100.

Figure 2008267779
Figure 2008267779

表２から明らかなように、本発明例の実施例１、２の伝熱管はいずれも溝（フィン）形状および耐圧強度が優れた。これは、比［Ｄ／ｔ］およびフィン底幅Ｗを適正に規定したため溝付加工時のメタルフローが良好だったことによる。特に比［Ｄ／ｔ］が１３．０〜１７．５の範囲内にあるＮｏ．４〜１１の伝熱管は溝（フィン）形状が極めて優れた。
伝熱特性（管内熱伝達率）については、実施例１、２の伝熱管はいずれも実用上問題のない特性を示した。実施例２の伝熱管はいずれも実施例１のＮｏ．５の伝熱管（α、β以外は同じ寸法）と較べて伝熱特性が劣った。これはフィンの頂角αおよびリード角βがより好ましい範囲（請求項２または３の規定範囲）を外れたためである。 As is apparent from Table 2, the heat transfer tubes of Examples 1 and 2 of the present invention example were excellent in the groove (fin) shape and pressure strength. This is because the metal flow during grooving was good because the ratio [D / t] and the fin bottom width W were appropriately defined. In particular, the ratio [D / t] is in the range of 13.0 to 17.5. The heat transfer tubes 4 to 11 were extremely excellent in groove (fin) shape.
Regarding the heat transfer characteristics (heat transfer coefficient in the tube), the heat transfer tubes of Examples 1 and 2 both exhibited practically no problem. The heat transfer tubes of Example 2 are all No. 1 of Example 1. The heat transfer characteristics were inferior to those of No. 5 heat transfer tubes (same dimensions except α and β). This is because the apex angle α and the lead angle β of the fin are out of the more preferable ranges (the prescribed range of claim 2 or 3).

一方、比較例１のＮｏ．１２の伝熱管は比［Ｄ／ｔ］が小さすぎたためフィンに亀裂や千切れが生じた。Ｎｏ．１３は比［Ｄ／ｔ］が大きすぎたため耐圧強度が低下した。比較例２のＮｏ．１４はフィンの底幅ｗが小さすぎたためフィンの形成が困難でフィンに亀裂が生じた。   On the other hand, no. In the heat transfer tube of No. 12, the ratio [D / t] was too small, so that the fins were cracked or broken. No. Since the ratio [D / t] of No. 13 was too large, the pressure resistance decreased. No. of Comparative Example 2 In No. 14, since the fin bottom width w was too small, it was difficult to form the fin, and the fin was cracked.

本発明の伝熱管の実施形態を示す説明図で、（イ）は横断面図、（ロ）は内面展開図、（ハ）は図１（ロ）のＡ−Ａ断面図である。BRIEF DESCRIPTION OF THE DRAWINGS It is explanatory drawing which shows embodiment of the heat exchanger tube of this invention, (A) is a cross-sectional view, (B) is an expanded inner surface figure, (C) is AA sectional drawing of FIG. 伝熱性能試験装置の概略図で、（イ）は蒸発試験用、（ロ）は凝縮試験用である。It is the schematic of a heat-transfer performance test apparatus, (A) is for an evaporation test, (B) is for a condensation test.

符号の説明Explanation of symbols

１ 伝熱管
２ 伝熱管内面のフィン
３ 伝熱管内面の溝 1 Heat Transfer Tube 2 Fin on Heat Transfer Tube Inside 3 Groove on Heat Transfer Tube Inside

Claims (3)

ＪＩＳＡ３０００系（Ａｌ−Ｍｎ系）アルミニウム合金からなる管内面にフィンが形成された伝熱管であって、前記伝熱管の外径（Ｄ）と底肉厚（ｔ）の比［Ｄ／ｔ］が１０．０以上、１７．５以下であり、かつ前記フィン底幅Ｗが０．１ｍｍ以上であることを特徴とする伝熱管。   A heat transfer tube in which fins are formed on the inner surface of a tube made of a JIS A3000 (Al-Mn) aluminum alloy, and the ratio [D / t] of the outer diameter (D) to the bottom wall thickness (t) of the heat transfer tube A heat transfer tube having a fin bottom width W of not less than 10.0 mm and not more than 10.0 and not more than 17.5. 請求項１に記載の伝熱管において、前記伝熱管の内面に形成されたフィンの頂角αが１８度以下であることを特徴とする伝熱管。   2. The heat transfer tube according to claim 1, wherein the apex angle α of the fin formed on the inner surface of the heat transfer tube is 18 degrees or less. 請求項１または２に記載の伝熱管において、前記伝熱管の内面に形成されたフィンのリード角βが２０度以上であることを特徴とする伝熱管。   3. The heat transfer tube according to claim 1, wherein a lead angle β of a fin formed on an inner surface of the heat transfer tube is 20 degrees or more. 4.
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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110132589A1 (en) * 2008-08-04 2011-06-09 Shun Yoshioka Heat exchanger grooved tube
JP2013011419A (en) * 2011-06-30 2013-01-17 Furukawa-Sky Aluminum Corp Method for manufacturing aluminum alloy made tube with inner face grooves for air conditioner
JP2018091610A (en) * 2016-11-30 2018-06-14 三菱アルミニウム株式会社 Heat transfer pipe, heat exchanger, and method for manufacturing heat transfer pipe
CN110763068A (en) * 2019-11-30 2020-02-07 广东美的制冷设备有限公司 Heat exchanger and air conditioner

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JPH085278A (en) * 1994-06-20 1996-01-12 Mitsubishi Shindoh Co Ltd Heat transfer tube with inner surface grooves
JPH09101093A (en) * 1995-10-02 1997-04-15 Mitsubishi Shindoh Co Ltd Heat transfer pipe with inner surface groove
JPH1054686A (en) * 1996-08-08 1998-02-24 Mitsubishi Shindoh Co Ltd Heat transfer tube with grooved inner surface and roll for manufacturing the same
JP2001289585A (en) * 2000-04-05 2001-10-19 Mitsubishi Alum Co Ltd Inner grooved aluminum tube and heat exchanger comprising the same
JP2002048487A (en) * 2000-08-01 2002-02-15 Mitsubishi Shindoh Co Ltd Heat transfer pipe with inner surface groove

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH085278A (en) * 1994-06-20 1996-01-12 Mitsubishi Shindoh Co Ltd Heat transfer tube with inner surface grooves
JPH09101093A (en) * 1995-10-02 1997-04-15 Mitsubishi Shindoh Co Ltd Heat transfer pipe with inner surface groove
JPH1054686A (en) * 1996-08-08 1998-02-24 Mitsubishi Shindoh Co Ltd Heat transfer tube with grooved inner surface and roll for manufacturing the same
JP2001289585A (en) * 2000-04-05 2001-10-19 Mitsubishi Alum Co Ltd Inner grooved aluminum tube and heat exchanger comprising the same
JP2002048487A (en) * 2000-08-01 2002-02-15 Mitsubishi Shindoh Co Ltd Heat transfer pipe with inner surface groove

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110132589A1 (en) * 2008-08-04 2011-06-09 Shun Yoshioka Heat exchanger grooved tube
JP2013011419A (en) * 2011-06-30 2013-01-17 Furukawa-Sky Aluminum Corp Method for manufacturing aluminum alloy made tube with inner face grooves for air conditioner
JP2018091610A (en) * 2016-11-30 2018-06-14 三菱アルミニウム株式会社 Heat transfer pipe, heat exchanger, and method for manufacturing heat transfer pipe
CN110763068A (en) * 2019-11-30 2020-02-07 广东美的制冷设备有限公司 Heat exchanger and air conditioner

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