JPH07305918A - Heat transfer pipe for absorber - Google Patents

Heat transfer pipe for absorber

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Publication number
JPH07305918A
JPH07305918A JP9838694A JP9838694A JPH07305918A JP H07305918 A JPH07305918 A JP H07305918A JP 9838694 A JP9838694 A JP 9838694A JP 9838694 A JP9838694 A JP 9838694A JP H07305918 A JPH07305918 A JP H07305918A
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Prior art keywords
heat transfer
tube
pipe
surface
transfer tube
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JP9838694A
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Japanese (ja)
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JP3617538B2 (en )
Inventor
Yoshihiro Nishimoto
Naoe Sasaki
直栄 佐々木
嘉弘 西本
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Sumitomo Light Metal Ind Ltd
住友軽金属工業株式会社
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00Tubular elements; Assemblies of tubular elements
    • F28F1/10Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40Tubular 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

Abstract

PURPOSE: To provide a heat transfer pipe for an air cooled absorber for directing an absorption fluid to flow down in the pipe wherein a greater effective heat transfer area is secured to improve heat transfer performance.
CONSTITUTION: A protrusion having a curved crosectional shape and a recessed part having a substantially discontinuous part on a bottom part on a cross section are formed on and in an inner peripheral surface of a heat transfer pipe 10 spirally at 5 to 75 lead angle (α) so as to be alternately positioned in the direction of a pipe periphery, and protrusion height of the protrusion with respect to the recessed part is made 0.2 to 0.6mm and pitches of the protrusions and recesses are made 1.0 to 5.0mm in the direction of the pipe periphery.
COPYRIGHT: (C)1995,JPO

Description

【発明の詳細な説明】 DETAILED DESCRIPTION OF THE INVENTION

【0001】 [0001]

【技術分野】本発明は、吸収式冷凍器や吸収式ヒートポンプ等の吸収器内に配管される伝熱管であって、特に、 TECHNICAL FIELD The present invention relates to a heat transfer tube that is piped to an absorption type refrigerator or an absorption type absorber in such a heat pump, in particular,
略鉛直方向に配管されて管内面に沿って吸収液が流下せしめられる一方、管外面に複数の冷却フィンが装着されて冷却空気が接触せしめられる空冷式の吸収器に用いられる伝熱管に関するものである。 While absorbing liquid substantially along the piping tube inner surface in the vertical direction is caused to flow down, relates the heat transfer tubes used in air-cooled absorber in which a plurality of cooling fins on the tube outer surface is brought into contact with the cooling air is mounted is there.

【0002】 [0002]

【背景技術】吸収式冷凍器や吸収式ヒートポンプ等の吸収器としては、従来から、一般に、管内に冷却水を流通せしめて、管外表面を流下せしめられる吸収液を冷却するようにした水冷式のものが採用されているが、近年、 As absorber such BACKGROUND absorption refrigerating unit and absorption heat pump is conventionally general, allowed circulating cooling water in the tube, water-cooled which is adapted to cool the absorbent is caused to flow down the pipe outside surface has been adopted as of but, in recent years,
小型化を図るために空冷式の吸収器が研究されており、 Air-cooled absorber to reduce the size have been studied,
家庭用の小型冷房機等への適用も検討されている。 It applied to the home for small cooling machine, and the like has been investigated.

【0003】ところで、空冷式の吸収器においては、冷却効率や吸収液の流通性の確保等の観点から、複数本の伝熱管を略鉛直方向に配管して、その管内面に沿って吸収液を流下させる一方、管外面に複数の冷却フィンを装着して冷却空気を接触せしめる構造が、好適に採用される。 [0003] In the air-cooled absorber, in view of securing the flow of the cooling efficiency and the absorption liquid, substantially in the pipe in the vertical direction a plurality of heat exchanger tubes, the absorption liquid along the pipe surface while allowing to flow down, structure brought into contact with cooling air by mounting a plurality of cooling fins on the tube outer surface is preferably employed.

【0004】ところが、かくの如き空冷式の吸収器においては、従来の水冷式の吸収器に用いられている内外面が平滑な円形断面の平滑管を伝熱管として採用すると、 [0004] However, in such air-cooled absorber thus, the inner and outer surfaces which are used in conventional water-cooled absorber employs a smooth tube of smooth circular section as a heat transfer tube,
吸収液が直線的に流下してしまい液膜が充分に広がらず、液膜の滞留時間も短くなるために充分な伝熱性能を得ることが難しい。 Absorbing liquid linearly flows down to cause the liquid film does not spread sufficiently, it is difficult to obtain sufficient heat transfer performance for even shorter residence time of the liquid film. そこで、特開平4−151473号公報に記載されているように平滑管の内表面を切削工具等で切り起こして局部的な突起を形成したり、管内表面に濡れ性向上のための表面処理を施したりすることが提案されているが、未だ、管周方向への広がりを充分に得ることができず、吸収液の滞留時間や管内表面の濡れ面積を確保することも難しいために、満足できる伝熱性能を得ることが困難であった。 Accordingly, or form a localized protrusion the inner surface of the smooth tube, as described in JP-A-4-151473 by cutting and raising the cutting tool or the like, a surface treatment for improving wettability to the tube surface While it or subjecting have been proposed, yet, it can not be obtained sufficiently spread to the circumferential direction of the pipe, in order that it is also difficult to ensure the wetted area of ​​the residence time and the tube surface of the absorption liquid, satisfactory it is difficult to obtain the heat transfer performance.

【0005】また、平滑管の内表面を切削工具で切り起こして管長手方向に連続して螺旋状に延びる突起を形成することによって、管内表面に螺旋状に延びる溝部を形成することも考えられるが、このような構造のものにあっては、吸収液が螺旋状の溝部に沿って管周方向に案内されて広げられるものの、切起しによって形成された突起が、鋭角的な頂角を有する略三角形の断面形状となるために、突起の表面に膜切れが生じ易く、液膜の厚さに偏りが生じて液膜の広がりが充分でなくなり、その結果、螺旋状の突起の形成によって管内表面積が増大されるにも拘わらず、全体としての伝熱性能の向上は余り望めなかったのである。 Further, by forming a projection extending helically continuous inner surface of the smooth tube in the longitudinal direction of the tube by cutting and raising the cutting tool, it is also conceivable to form grooves extending helically in the tube surface there, the apparatus having such a structure, although the absorption liquid is expanded is guided by the circumferential direction of the pipe along the spiral groove, projections formed by the cut and raised, a sharp apex angle for the cross-sectional shape of substantially triangular with, film breakage easily occurs on the surface of the protrusion, the spread of the liquid film becomes insufficient to cause deviation in thickness of the liquid film, resulting in the formation of helical projection despite the tube surface area is increased, it was not expected so much improvement in the heat transfer performance overall.

【0006】或いはまた、管内にコイル部材を挿入して管内周面に密接配置することによって、管内表面に螺旋状に延びる溝部を形成することも考えられるが、このような構造のものにあっては、コイル部材の管内表面への密着性を安定して得難いために、性能の安定性や耐久性に問題があり、しかも、管内にコイル部材を配設するには、伝熱管とは別途コイル部材を準備し、それを伝熱管内に挿入した後、かかるコイル部材を管内表面に密接させる加工をしなければならないために、製造が極めて面倒であるという問題もあった。 [0006] Alternatively, by closely arranged in a tube periphery by inserting the coil member into the tube, it is conceivable to form grooves extending helically in the tube surface, the apparatus having such a structure in order inaccessible adhesion to the tube surfaces of the coil member stably, there are problems in stability and durability performance, moreover, to dispose the coil member in the tube is, separately from the heat exchanger tube coil prepare the member, after it was inserted into the heat transfer tube, in order to have to machining to close such coil member in the tube surface, there is a problem that manufacturing is extremely cumbersome.

【0007】 [0007]

【解決課題】ここにおいて、本発明は、上述の如き事情を背景として為されたものであって、その解決課題とするところは、略鉛直方向に配管した場合でも、管内を流下せしめられる吸収液の滞留時間を充分に得ることができると共に、管内表面において液膜の著しい偏りを生ずることなく有効な濡れ面積を確保することができ、有効伝熱面積が増加されて伝熱性能の向上が達成され得る吸収器用伝熱管を提供することにある。 A problem] Here, the present invention is, was made of such circumstances described above as a background, a place to its problem to be solved, even if the pipe in a substantially vertical direction, the absorption liquid which is caused to flow down the tube it is possible to obtain the residence time of the sufficiently effective wetting area without causing significant deviation of the liquid film can be secured in the tube surface, effective heat transfer area is increased achieved improvement in the heat transfer performance It is to provide an absorbent dexterity heat transfer tube may be.

【0008】 [0008]

【解決手段】そして、かかる課題を解決するために、本発明は、略鉛直方向に配管されて吸収液が管内面に沿って流下せしめられる一方、管外面に複数の冷却フィンが装着されて冷却空気が接触せしめられる空冷式の吸収器用伝熱管において、5〜75°のリード角で管内面を管長手方向に向かって螺旋状に延びる凹部と凸部を、管周方向で交互に位置するように、それぞれ管周方向で1. SOLUTION] In order to achieve the foregoing object, the present invention is substantially while vertically plumbed absorption liquid is made to flow down along the inner surface, a plurality of cooling fins are mounted on the tube outside surface cooling the absorbent dexterity heat transfer tube of the air-cooled air is brought into contact, the concave and convex portions extending toward the inner surface in the longitudinal direction of the tube in a spiral lead angle of 5 to 75 °, so as to be positioned alternately in the circumferential direction of the pipe to, 1 each tube circumferential direction.
0〜5.0mmのピッチで形成すると共に、該凸部の凹部に対する突出高さを0.2〜0.6mmとする一方、かかる凸部の表面を湾曲断面形状とし、且つ凹部の底部を実質的な不連続部を有する断面形状としたことを、特徴とするものである。 And forming a pitch of 0~5.0Mm, while the 0.2~0.6mm the protrusion height to the recess of the convex portion, the surface of such protrusions and curved cross-sectional shape, and substantially the bottom of the recess that it has a cross-sectional shape having a discontinuity portion and is characterized.

【0009】そこにおいて、凸部の断面形状としては、 [0009] Therein, the cross-sectional shape of the convex portion,
半円形状や半楕円形状,放物線形状等が何れも採用され得る。 Semicircular or semi-elliptical shape, even a parabolic shape or the like either may be employed. また、そのような凸部を、管軸方向一方の側に傾斜して設けるようにしても良い。 Moreover, such a protrusion may be provided to be inclined to one side in the tube axis direction.

【0010】さらに、凹部および凸部のリード角よりも小さなリード角を有するコイル部材を管内に挿入し、該コイル部材を管内周面に密接させて配設することも可能である。 Furthermore, by inserting a coil member having a smaller lead angle than the lead angle of the concave and convex portions in the tube, it is also possible to arrange by close contact with the coil member into the tube circumference.

【0011】 [0011]

【発明の具体的構成】先ず、図1〜3には、本発明に従う構造とされた吸収器用伝熱管の一具体例が示されている。 [Specific Configuration of the Invention] First, in FIGS. 1-3, one embodiment of the construction according to the present invention absorbs dexterity heat transfer tube is illustrated. かかる伝熱管10は、全体として円形断面の直管形状を有しており、図4に示されているように、適当な長さに切断されて複数本が互いに所定距離を隔てて配管されると共に、それらの外周面にプレートフィン12が装着されて一体的に組み付けられることにより、空冷式の吸収器を構成するようになっている。 Such heat transfer tube 10 has a straight tube shape of a circular cross-section as a whole, as shown in FIG. 4, is a pipe at a predetermined distance plurality of mutually are cut to appropriate length together, by being integrally assembled with the plate fin 12 is attached to their outer circumference, so as to constitute a air-cooled absorber. そして、各伝熱管10の軸心が略鉛直方向に延びる状態で吸収器内に配設され、管内面に沿って吸収液14が流下されることにより、管内に導かれた冷媒が吸収液に吸収されるようにする一方、管外面およびプレートフィン12に冷却空気が接触せしめられて、冷媒の吸収液への溶解によって生ずる溶解熱乃至は希釈熱や潜熱による温度上昇が抑えられることにより、吸収器として機能せしめられるようになっている。 Then, the axis of each heat transfer tube 10 is disposed to the absorber in a state extending substantially in the vertical direction, by the absorption liquid 14 is flowing down along the inner surface of the tube, the refrigerant introduced into the tube within the absorption liquid while to be absorbed, it is brought into contact with the cooling air outside the tube surface and plate fins 12, by the heat of dissolution to occur by dissolution of the absorption liquid refrigerant temperature rise can be suppressed by heat of dilution and latent heat absorption adapted to be brought into function as a vessel.

【0012】ここにおいて、伝熱管10の材質は、従来と同様、使用する冷媒および吸収剤に対する耐蝕性や伝熱性,加工性等を考慮して選定されることとなり、例えば、水を冷媒とし、臭化リチウムを吸収剤とする場合には、銅管が好適に採用され得る。 [0012] In this case, the material of the heat transfer tube 10, like the prior art, will be selected in consideration of corrosion resistance and heat transfer for the refrigerant and the absorbent used, the processability and the like, for example, using water as the refrigerant, when lithium bromide and absorbent, copper pipe may be suitably employed. また、この伝熱管10 In addition, the heat transfer tube 10
は、図1中のA部の拡大図および横断面拡大図が図2および図3に示されているように、外周面16が平滑面とされている一方、内周面に対して、それぞれ管長手方向に螺旋状に延びる複数条の凹部18と凸部20が、管周方向で交互に位置して互いに略平行に形成されている。 , As the enlarged view and a side cross-sectional enlarged view of the A portion in FIG. 1 is shown in Figures 2 and 3, while the outer peripheral surface 16 is a smooth surface, the inner peripheral surface, respectively recess 18 and the convex portion 20 of plural rows extending helically pipe longitudinal direction are substantially parallel to each other are located alternately in a tubular circumferential direction.

【0013】これら凹部18と凸部20は、図面上に明示されてはいないが、管周方向におけるピッチ:p(図3参照)、換言すれば管軸に直角な断面において周方向で隣接位置する凹部18と凹部18および凸部20と凸部20の間隔が、何れも1.0〜5.0mmとなるように設定される。 [0013] These recesses 18 and protrusions 20, although not explicitly in the drawings, the pitch in the circumferential direction of the pipe: p (see FIG. 3), adjacent positions in the cross section perpendicular to the tube axis in other words in the circumferential direction spacing of the recesses 18 and the recesses 18 and the projections 20 and the projections 20 is set so as to both become 1.0 to 5.0 mm. 具体的には、例えば、φ19.05mmの銅管であれば、凹部18および凸部20の数が、それぞれ、一周当たり12〜48条となるように設定されることとなる。 Specifically, for example, if the copper tube Fai19.05Mm, number of recesses 18 and protrusions 20, respectively, will be set so that 12 to 48 Article per round.

【0014】けだし、かかるピッチ:pが、1.0mmより小さいと、凹部18の幅が小さくなり過ぎて、臭化リチウム水溶液等の粘性の高い溶液が凹部18内に充分に流れ込みにくくなり、凹部18に沿った管周方向への液膜の広がりが充分に期待できなくなるからであり、一方、ピッチ:pが、5.0mmより大きいと、管内面に形成される凹凸が少なくなって有効な伝熱面積の増加が実現され難くなるからである。 [0014] capped, such pitch: p is a 1.0mm smaller, too the width of the recess 18 is small, high viscosity, such as lithium bromide aqueous solution is less likely to flow sufficiently into the recess 18, the recess spreading of liquid film in the circumferential direction of the pipe along the 18 is because not be sufficiently expected, whereas, pitch: p is a 5.0mm larger, it becomes less irregularities formed on the tube surface active This is because the increase in heat transfer area is not easily achieved. 即ち、凹部18および凸部20の管周方向におけるピッチ:pを、1.0〜5.0 That is, the pitch in the circumferential direction of the pipe in the recess 18 and the protrusion 20: a p, 1.0 to 5.0
mmとすることにより、それら凹部18および凸部20の形成による管内面の伝熱面積の増加と、凹部18の案内作用による管周方向への液膜の広がりの促進とが、共に有利に達成されて、有効伝熱面積の拡大が効果的に図られ得るのである。 With mm, and the increase of heat transfer area of ​​the tube surface due to the formation of their recesses 18 and protrusions 20, and the promotion of the spread of the liquid film in the circumferential direction of the pipe due to the guiding action of the recess 18 are both advantageously achieved is is the enlargement of the effective heat transfer area can be reduced effectively.

【0015】また、これら凹部18と凸部20は、伝熱管10の全長に渡って一定のリード角で形成されていても、或いは部分的にリード角が変化させられていても良いが、かかるリード角:αが、何れの部位においても5 Further, the recesses 18 and the projections 20 may be over the entire length of the heat transfer tube 10 is formed at a predetermined lead angle, or partially but lead angle may be allowed to change, such lead angle: α is, in any of the sites 5
〜75°の範囲内となるように、好ましくは5〜30° So as to be in the range of to 75 °, preferably 5 to 30 °
の範囲内となるように設定される。 It is set to be within a range of. なお、リード角:α It should be noted that the lead angle: α
とは、図1に示されているように、凹部12または凸部14の接線と、管軸に直角な平面とがなす角度をいう。 And, as shown in FIG. 1, it referred to the tangent of the concave portion 12 or convex portion 14, the angle between a plane perpendicular to the tube axis.

【0016】けだし、リード角:αが75°より大きいと、伝熱管10を吸収器に組み付けた際に、凹部12に沿う吸収液の流下速度が大きくなって、管内面における液膜の滞留時間を充分に確保することが難しくなるからであり、一方、リード角:αが5°より小さいと、伝熱管10の内周面における凹部12および凸部14の形成が困難となるからである。 [0016] kicking, lead angle: alpha is greater than 75 °, when assembling the heat transfer tube 10 to the absorber, increases the flow-down speed of the absorbent along the recessed portion 12, the residence time of the liquid film in the tube surface the is because it is difficult to sufficiently secure, whereas, lead angle: alpha and is less than 5 °, since formation of the recesses 12 and protrusions 14 on the inner circumferential surface of the heat transfer tube 10 becomes difficult. 即ち、凹部18および凸部2 That is, the concave portion 18 and convex portion 2
0のリード角:αを、5〜50°とすることにより、より好ましくは5〜30°とすることにより、製作性の著しい低下を伴うことなく、管内面を流下せしめられる液膜が凹部12に沿って管周方向に導かれて液膜の流下速度が効果的に抑えられると共に、流下距離が実質的に増大されて、吸収液の滞留時間を有利に確保することができるのである。 0 lead angle: the alpha, by a 5 to 50 °, by more preferably to 5 to 30 °, without significant reduction of manufacturability, the recess 12 the liquid film is caused to flow down the tube surface falling speed of the tube circumferentially guided by liquid film with suppressed effectively along, falling distance is substantially increased, it is possible to advantageously ensure a residence time of the absorbent.

【0017】さらに、凹部18には、その断面において、実質的な不連続部22が底部に形成されている。 Furthermore, the recess 18, in its cross-section, substantial discontinuity 22 is formed at the bottom. この不連続部22は、凹部18の横断面において、共通接線を持たない交点で連接された屈曲点状の連接部として形成され、或いは、曲率半径が3.5mm以下である湾曲面や、幅が2.5mm以下である平坦面の如く、実質的に屈曲点とみなし得る連接部として形成される。 This discontinuity 22, in cross-section of the recess 18, is formed as a connecting part of the articulated bending point shape at the intersection that does not have a common tangent, or curved surface and the curvature radius is less than 3.5 mm, a width There as flat surfaces is 2.5mm or less, is formed as a connecting part which can be regarded substantially bending points.

【0018】すなわち、このような実質的な不連続部2 [0018] That is, such a substantial discontinuity 2
2を凹部18の底部に形成すれば、かかる凹部18の底部において、伝熱管10の長手方向に向かって螺旋状に延びる筋状の細溝が構成されることとなり、その結果、 By forming 2 the bottom of the recess 18, at the bottom of such recesses 18, will be streaky narrow groove extending spirally toward the longitudinal direction of the heat transfer tube 10 is constituted, as a result,
管内面を流下せしめられる吸収液が、その表面張力等に基づく毛細管現象によって、かかる細溝に沿って凹部1 Absorbent is caused to flow down the tube surface, by capillary action based on the surface tension, along with such narrow groove recess 1
8内を管周方向に螺旋状に広がるのであり、その結果、 Within 8 is a spread in a spiral circumferential direction of the pipe, as a result,
吸収液の凹部18および凸部20に沿った管周方向への流れが促進されて、液膜の管周方向への広がりや滞留時間の延長が図られ、有効伝熱面積、延いては伝熱性能が有利に向上され得るのである。 Absorbing liquid recess 18 and flows in the circumferential direction of the pipe along the convex portion 20 is promoted, and the extension of the spreading and the residence time in the pipe circumferential direction of the liquid film is achieved, the effective heat transfer area, by extension Den is the thermal performance can be advantageously improved.

【0019】なお、かかる凹部18の底部は、その断面形状において、実質的な不連続部22を挟んだ両側内面の交角を20〜90°とすることが望ましい。 [0019] Incidentally, the bottom of such a recess 18, in its cross-sectional shape, it is preferable that the intersection angle of substantially bilateral inner surface sandwiching the discontinuities 22 and 20 to 90 °. それによって、毛細管現象による吸収液の管周方向への広がりの促進効果が一層有利に発揮され得るのである。 Thereby, the effect of promoting the spread of the circumferential direction of the pipe of the absorbent by capillary phenomenon is as it can be more advantageously exhibited.

【0020】また、凸部20は、湾曲断面形状をもって形成されている。 Further, the convex portion 20 is formed with a curved cross-sectional shape. 即ち、かかる凸部20の表面は、その横断面の全体に渡って曲率半径が一定である必要はないが、連続しており、例えば、半円形状や半楕円形状,放物線形状などの断面形状が好適に採用され得る。 That is, the surface of such protrusions 20, the but throughout the radius of curvature of the cross section need not be constant, are continuous, for example, semicircular or semi-elliptical cross-sectional shape such as parabolic It can be suitably employed.

【0021】すなわち、凸部20を、このような湾曲断面形状をもって形成すれば、吸収液が凸部20を乗り越えて鉛直下方に流下する際にも、その流れがスムーズで、表面張力の作用によって略均一の厚さの液膜が有利に形成されて、部分的な膜厚の偏りや渇き面(液切れ) [0021] That is, the convex portion 20, when formed with such a curved cross-sectional shape, when the absorption liquid flows down vertically downward over the convex portion 20 is also the flow smooth, by the action of surface tension substantially is the thickness of the liquid film advantageously formed of homogeneous, partial thickness bias and thirst plane (solution break)
の発生が効果的に防止され得るのであり、その結果、濡れ面積が有利に確保されると共に、液膜厚さの大きな偏りによる部分的な熱伝導の低下が回避されて、有効伝熱面積の増加による伝熱性能の向上がより有効に達成され得るのである。 Generation is as it can be effectively prevented, as a result, the wetting area is advantageously ensured, a partial reduction in the thermal conductivity due to a large deviation of the liquid film thickness is avoided, the effective heat transfer area is the improvement in the heat transfer performance can be more effectively achieved by an increase.

【0022】なお、凸部20の表面を、その全体に渡って、変曲点を有しない断面形状とすると共に、そのような断面形状をもって形成されて隣接位置せしめられた凸部20,20の表面を、実質的な不連続部22によって直接的に接続せしめてなる断面形状とすることも可能である。 [0022] Incidentally, the surface of the convex portion 20, throughout its, as well as to have no cross-sectional shape of the inflection point, of the convex portions 20, 20 which are brought adjacent positions are formed with such a cross-section the surface can also be a cross-sectional shape formed by brought directly connected by substantial discontinuities 22. そして、凹部18および凸部20を、このような断面形状をもって形成すれば、凹部18の底部に沿った吸収液の管周方向への広がりと、凸部20の表面における略均一な液膜の形成とが、何れも、極めて有効に達成され得るのこととなる。 Then, the concave portion 18 and convex portion 20, when formed with such a cross-sectional shape, and spread in the circumferential direction of the pipe of the absorbent along the bottom of the recess 18, a substantially uniform liquid film on the surface of the convex portion 20 formation and are both, it comes to be very effectively achieved.

【0023】さらに、凸部20は、凹部18の底面からの突出高さが0.2〜0.6mmとなるように形成される。 Furthermore, the convex portion 20, the protruding height from the bottom surface of the recess 18 is formed so as to be 0.2 to 0.6 mm.

【0024】けだし、凸部20の突出高さが0.2mmより低いと、臭化リチウム溶液等の比重が大きい吸収液を凹部18内に有効に保持することが難しく、結果的に、 The kicking, the protrusion height of the convex portion 20 is less than 0.2 mm, it is difficult to effectively retain the absorbed liquid specific gravity is greater, such as lithium bromide solution in the recess 18, resulting in,
凹部18に沿った吸収液の管周方向への広がり効果が低下してしまうからであり、一方、凸部20の突出高さが0.6mmより高いと、伝熱管10の内周面における凹部12および凸部14の形成が困難となるからである。 Is because broadening effect on the pipe circumferential direction of the absorbent along the recessed portions 18 is reduced, whereas, if the projecting height of the convex portion 20 is higher than 0.6 mm, the recess in the inner circumferential surface of the heat transfer tube 10 formation of 12 and protrusions 14 is from difficult. 即ち、凸部20の突出高さを、0.2〜0.6mm、好ましくは0.3〜0.4mmとすることにより、良好なる製作性を確保しつつ、凹部18に沿った管周方向への液膜の広がりの促進による有効伝熱面積の拡大が効果的に図られ得るのである。 That is, the protrusion height of the convex portion 20, 0.2 to 0.6 mm, preferably by a 0.3 to 0.4 mm, while maintaining good Naru manufacturability, peritubular direction along the recess 18 enlargement of the effective heat transfer area by a liquid film spreading of promotion of is as it can be achieved effectively.

【0025】なお、吸収液を凹部18内に有利に保持せしめて、吸収液の凹部18に沿った管周方向への広がりを促進するためには、図5に示されているように、凸部20を、管軸方向一方の側に傾斜して突出形成することも有効である。 It should be noted, the absorbent liquid brought advantageously retained within the recess 18, so in order to promote the spread of the circumferential direction of the pipe along the recess 18 of the absorption liquid is shown in Figure 5, the convex the parts 20, it is also effective to protrude to be inclined to one side in the tube axis direction. 即ち、かくの如き傾斜した凸部20を形成し、かかる凸部20が鉛直上方に向かって傾斜するように伝熱管10を配管すれば、管内面に沿って流下せしめられる吸収液を凸部20が受ける形となるのであり、 That is, to form a convex portion 20 that such inclination of nuclear, if pipe heat transfer tube 10 as according protrusion 20 is inclined toward the vertically upward, the convex portion of the absorbent is caused to flow down along the inner surface 20 It is than the form that is subjected,
それ故、液膜が凹部18内に有利に保持されて、凹部1 Therefore, the liquid film is advantageously held in the recess 18, the recess 1
8に沿った液膜の管周方向への広がりや滞留時間の延長が、一層効果的に達成され得るのである。 It spreads and residence time extension of the tube circumferential direction of liquid film along the 8 is as it can be more effectively achieved.

【0026】また、図面上に明示はされていないが、上述の如き凹部18と凸部20が形成された伝熱管10に対して、凹部18および凸部20のリード角:αよりも小さなリード角を有する螺旋状のコイル部材を挿入し、 Further, although not explicitly shown in the drawing, with respect to the heat transfer tube 10 of the recess 18 and the convex portion 20 such as described above is formed, the lead angle of the concave portion 18 and convex portion 20: Small than α leads insert the helical coil member having a corner,
凸部20に密接させて配設することも可能である。 It is also possible to arrange by close contact with the projections 20. このようなコイル部材を配設することにより、伝熱面積の更なる増大が図られ得ると共に、吸収液がコイル部材に沿って管周方向に導かれることにより吸収液の滞留時間の更なる増大が図られ得るのである。 By disposing such a coil member, increases with a further increase of the heat transfer area can be reduced, the absorption liquid is further residence time of the absorbent by being guided in the pipe circumferential direction along the coil member is the can achieved.

【0027】なお、かかるコイル部材は、伝熱管10と同様、冷媒や吸収剤に対する耐蝕性等を考慮して材質が選定されることとなり、例えば、凹部18および凸部2 [0027] Incidentally, such a coil member, like the heat transfer tube 10, will be made by considering the corrosion resistance and the like for refrigerant and absorbent are selected, for example, recesses 18 and protrusions 2
0が形成された伝熱管10内に挿入された後、拡管プラグ等を挿入して、コイル部材を伝熱管10の内周面に圧接固定すること等によって、伝熱管10に組み付けられる。 After 0 is inserted into the heat transfer tube 10 which is formed, by inserting a tube expanding plug, etc., such as by press fixing the coil member to the inner peripheral surface of the heat transfer tube 10 is assembled to the heat transfer tube 10.

【0028】ところで、このような伝熱管10は、内外周面が平滑な素管に対して、目的とする凹部18および凸部20に対応した螺旋状の凹凸が外周面に付されたプラグを用い、引抜加工を施すこと等によっても製造することが可能であるが、特に、転造加工によって有利に製造され得る。 By the way, such heat transfer tube 10, to the inner peripheral surface smooth base tube, a plug is helical irregularities corresponding attached to an outer peripheral surface in the recess 18 and the protrusion 20 for the purpose used, although it is also possible to manufacture such as by applying a drawing process, in particular, it may be advantageously produced by the rolling process.

【0029】具体的には、例えば、図6〜8に示されているように、内外周面が平滑な素管24の内部に、目的とする凹部18および凸部20に対応した螺旋状の凹凸が外周面に付されたプラグ26を挿入配置すると共に、 [0029] Specifically, for example, as shown in Figure 6-8, the interior of the inner peripheral surface smooth base tube 24, a spiral corresponding to the recesses 18 and protrusions 20 for the purpose with irregularities inserts disposed a plug 26 attached to the outer peripheral surface,
素管24の外部に3つのロール26を配設せしめて、それらロール26によって素管24の外周面に圧力を加え、素管24を回転させながら軸方向に移動させて管内周面に凹凸加工を施すことにより、目的とする伝熱管1 And allowed disposed external to the three rolls 26 of base pipe 24, the pressure on the outer peripheral surface of the base pipe 24 by the rolls 26, the roughened while rotating the blank tube 24 is moved axially into the tube circumference by the applied heat transfer tubes 1 of interest
0が製造されることとなる。 0 is to be produced.

【0030】なお、ロール26としては、外周面が平滑な異径のディスク28の複数枚を軸方向に重ね合わせてロッド30に装着したものが好適に用いられ、一般的な転造加工と同様、ロッド30の軸が管軸に対して所定角度:βだけ傾斜した状態で配設される。 [0030] As the roll 26, the outer peripheral surface causes are preferably used those attached to the rod 30 by overlapping a plurality of sheets of smooth different diameter disks 28 in the axial direction, like a typical rolling process , the predetermined angle the axis of the rod 30 to the tube axis: is arranged in a state of β inclined by. このようなロール26を採用すれば、各種サイズの伝熱管の転造加工に、容易に対応することができるのである。 By employing such a roll 26, the rolling of the heat transfer tubes of various sizes, it is possible to easily correspond.

【0031】すなわち、上述の如き構造の伝熱管10にあっては、転造加工等によって容易に製造することができるのであり、それ故、従来の切起し突起を設けた伝熱管に比べて、製造性およびコスト性が大幅に向上されるといった利点も有しているのである。 [0031] That is, in the heat transfer tube 10 of constructed as described above, rolling process is as it can be readily prepared by, therefore, as compared with the heat transfer tube having a conventional cut-and-raised projection is the productivity and cost property also has advantage is greatly improved.

【0032】そして、上述の如き伝熱管10は、図4に示されているように、アルミニウム合金等で形成された多数枚のプレートフィン12の装着孔に挿通固定されることにより、それらのプレートフィンが伝熱管10の外周面に装着されると共に、複数本が並列的に配置された状態でプレートフィン12によって一体的に組み付けられることとなる。 [0032] Then, such heat transfer tube 10 described above, as shown in FIG. 4, by being inserted and fixed in the mounting hole of a number formed by the aluminum alloy sheet of plate fins 12, the plates with fins are mounted on the outer peripheral surface of the heat transfer tube 10, so that the assembled integrally by a plate fin 12 in a state where the plurality of are arranged in parallel. なお、かかるプレートフィン12の装着は、例えば、伝熱管10に多数枚のプレートフィン1 Incidentally, the mounting of such plate fin 12 is, for example, large number of plate fins 1 in the heat transfer tube 10
2を挿通せしめた後、伝熱管10内に拡管プラグを挿入して拡径し、プレートフィン12の装着孔に嵌着せしめることによって行われることとなる。 After allowed through 2, and enlarged by inserting a tube expanding plug into the heat transfer tube 10, and thus performed by caulking clothed fitted into the mounting holes of the plate fins 12.

【0033】以上、本発明の構成について、図面を参照しつつ詳細に説明したが、本発明は、図示された具体例や上述の具体的構成例、或いは以下の実施例の記載によって限定的に解釈されるものではなく、当業者の知識に基づいて種々なる変更,修正,改良等を加えた態様において実施され得るものであり、また、そのような実施態様が、本発明の趣旨を逸脱しない限り、何れも、本発明の範囲内に含まれるものであることが、理解されるべきである。 [0033] Although the structure of the present invention has been described in detail with reference to the accompanying drawings, the present invention is limited to specific examples and specific configuration of the above illustrated, or by the description of the following examples not to be interpreted with various changes based on the knowledge of those skilled in the art, modifications are those may be implemented in aspects mutatis improvement etc. Moreover, such embodiments are not departing from the gist of the present invention unless both, that are intended to be included within the scope of the present invention, it should be understood.

【0034】 [0034]

【実施例】JIS H3300の銅管(外径:φ19. EXAMPLES copper tube JIS H3300 (outer diameter: φ19.
05mm,肉厚:0.7mm)を素管として用い、図6〜8 05Mm, wall thickness: 0.7 mm) used as the base pipe, 6-8
に示されている如き転造加工を施して、管内面に凹部および凸部を形成することにより、図1〜3に示されている如き構造の伝熱管を得た。 Subjected to have such thread rolling shown in, by forming recesses and projections on the inner surface of the tube to obtain a heat transfer tube of such structures are shown in FIGS. なお、かかる伝熱管における凹部および凸部の数はそれぞれ一周当たり24条で、 In Article 24 per round each number of recesses and protrusions in such heat transfer tube,
ピッチ:pを略2.5mmとし、リード角:αを15°, Pitch: p was approximately 2.5 mm, the lead angle: alpha of 15 °,
凹部の底面に対する凸部の高さを略0.3mmとした。 The height of the convex portion with the bottom surface of the concave portion has a substantially 0.3 mm. また、凸部を、曲率半径が2.2mmの略半円形の断面形状とすると共に、凹部の底部に曲率半径が0.1mmである実質的な不連続部を形成し、かかる不連続部によって、 Further, a convex portion, with the curvature radius of the substantially semi-circular cross-sectional shape of 2.2 mm, radius of curvature at the bottom of the recess to form a substantially discontinuous portion is 0.1 mm, by such discontinuities ,
隣接する両側凸部が直接に接続されてなる断面形状を採用した。 Both side convex portions adjacent adopted a cross-sectional shape formed by connecting directly. なお、凸部は管軸方向に傾斜させず、管内へのコイル部材の配設も行わなかった。 Incidentally, the convex portion is not inclined in the axial direction of the tube, was not even arrangement of the coil member into the tube.

【0035】また、かくの如き本実施例の伝熱管と比較するために、同一の素管の内周面を切起し加工することにより、図9に示されているように、螺旋条に連続して延びる切起し突起32を管内周面に設けた比較例としての伝熱管34を得た。 Further, for comparison with the heat transfer tube of the present embodiment, such as nuclear, by cut-and-raised working an inner peripheral surface of the same base pipe, as shown in Figure 9, the helical strip the cut and raised projections 32 extending continuously to obtain a heat transfer tube 34 as a comparative example in which the tube circumference. なお、かかる伝熱管34における切起し突起32の数(ピッチ)やリード角、突出高さは、何れも、上記本実施例の伝熱管における凸部と同一に設定した。 Note that the number (pitch) and the lead angle of the cut-and-raised projection 32 in such heat exchanger tubes 34, the protruding height are both set to the same and the convex portion of the heat transfer tube of the present embodiment.

【0036】そして、これら本実施例および比較例の伝熱管を各1本用い、それぞれ、管外周面にアルミニウムフィンを装着せしめて鉛直方向に配管し、濃度:64重量%,飽和圧力:8.9mmHgの臭化リチウム水溶液を、管内周面に沿わせて60cc/分の流量で流下させる一方、35℃(入口温度)の冷却空気をアルミニウムフィンに連続的に接触させて冷却せしめつつ、伝熱管内に水蒸気を導いて水蒸気の吸収能力を測定した。 [0036] Then, using the heat transfer tube of the present Example and Comparative Example 1 each, respectively, and piping in the vertical direction allowed attached aluminum fins Kangaishu surface, concentration: 64 wt%, the saturation pressure: 8. lithium bromide aqueous solution of 9 mmHg, while to flow down along a tube circumference at 60 cc / min flow rate, 35 ° C. the cooling air (inlet temperature) while allowed to cool by continuous contact with the aluminum fin, heat transfer It led to the water vapor to measure the absorption capacity of the water vapor in the tube. かかる測定結果を、冷房能力が2.2kW時の発生蒸気を完全に吸収した場合の吸収能力に対する比率で表した結果が、 Such measurements, results expressed as a percentage of the absorption capacity in the case of cooling capacity has completely absorbed the steam generated at the time of 2.2kW is,
下記「表1」に示されている。 It is shown in the following "Table 1".

【0037】 [0037]

【0038】かかる比較実験結果からも、本発明に従う構造とされた伝熱管が、優れた伝熱性能を有しており、 [0038] From such a comparison experiment result, heat transfer tube constructed according to the present invention, has excellent heat transfer performance,
空冷式吸収器に用いた場合に優れた水蒸気の吸収能力を発揮し得ることが明らかである。 It is clear that can exhibit the absorption capacity of the excellent water vapor when used for air-cooled absorber.

【0039】 [0039]

【発明の効果】上述の説明から明らかなように、本発明に従う構造とされた吸収器用伝熱管においては、凹部の底部が管長手方向に螺旋状に延びる筋状の細溝形状をもって形成されていることから、鉛直方向に配管された際、管内面を流下せしめられる液膜が凹部に沿って導かれることにより、管周方向に広げられて流下距離が長くされると共に、流下速度が抑えられて滞留時間が有利に確保されるのであり、しかも、凸部の表面にも略均一な膜厚さで広げられることから、液膜が広い面積で形成されて有効伝熱面積が効果的に確保されるのであり、それによって、優れた伝熱性能が発揮され得るのである。 [Effect of the Invention] As apparent from the above description, in the absorbent dexterity heat exchanger tube constructed according to the present invention, is formed with a streaky narrow groove-shaped bottom of the recess extends helically pipe longitudinal direction since you are, when plumbed in the vertical direction, by the liquid film is caused to flow down the tube surface is directed along the recess, the falling distance is widened in the circumferential direction of the pipe is long, falling speed is suppressed residence time Te is of being advantageously ensured, moreover, since the spread at a substantially uniform film thickness on the surface of the convex portion, the effective heat transfer area is effectively formed liquid film in a large area reserved and of being, whereby it's excellent heat transfer performance can be exhibited.

【0040】また、凸部を管軸方向一方の側に傾斜させれば、配管時に、管内面に沿って流下せしめられる吸収液を、かかる凸部によって受ける形とすることができるのであり、それによって、液膜が凹部内に有利に保持されて、液膜の管周方向への広がりや滞留時間の延長が、 Further, if the inclined convex portion on one side in the tube axis direction, when the pipe, the absorbing fluid is caused to flow down along the inner surface, and as it can be in the form to receive by such protrusions, it the liquid film is advantageously held in the recess, the extension of the spreading and the residence time in the pipe circumferential direction of the liquid film,
より効果的に図られ得る。 More can be effectively achieved.

【0041】更にまた、伝熱管の内部にコイル部材を密接配置すれば、伝熱面積の更なる増大が図られると共に、吸収液の滞留時間の更なる延長が図られ得る。 [0041] Furthermore, if the internal closely arranged coil member of the heat transfer tube, with a further increase of the heat transfer area is achieved, the further extension of the residence time of the absorbent may be achieved.

【図面の簡単な説明】 BRIEF DESCRIPTION OF THE DRAWINGS

【図1】本発明に従う構造とされた伝熱管の具体例を示す一部切欠正面図である。 1 is a partially cutaway front view showing a specific example of the structure has been heat transfer tube according to the present invention.

【図2】図1におけるA部を拡大して示す断面説明図である。 Is a cross-sectional view showing an enlarged portion A of FIG. 1;

【図3】図1に示された伝熱管の横断面を拡大して示す説明図である。 3 is an explanatory view showing an enlarged cross section of the heat transfer tube shown in FIG. 1.

【図4】図1に示された伝熱管に対するプレートフィンの組付状態を示す説明図である。 4 is an explanatory diagram showing an assembled state of the plate fins for heat transfer tubes shown in FIG.

【図5】本発明に従う構造とされた伝熱管の別の具体例を示す、図2に対応する断面説明図である。 Figure 5 shows another embodiment of the structure has been heat transfer tube according to the present invention, it is a cross-sectional view corresponding to FIG.

【図6】図1に示された伝熱管の製造装置の一例を説明するための縦断面説明図である。 6 is a longitudinal sectional view for explaining an example of an apparatus for producing a heat transfer tube shown in FIG. 1.

【図7】図6に示された伝熱管の製造装置の正面説明図であって、図6における VII−VII 断面に相当する図である。 [7] A front view of an apparatus for manufacturing a heat transfer tube shown in FIG. 6 is a view corresponding to the section taken along line VII-VII in FIG.

【図8】図6に示された伝熱管の製造装置におけるロールの配設状態を示す説明図である。 8 is an explanatory diagram showing an arrangement state of the roll in the apparatus for manufacturing a heat transfer tube shown in FIG.

【図9】伝熱性能の実験において比較例として用いた伝熱管を示す、図2に対応する断面説明図である。 It shows a heat transfer tube used as a comparative example in FIG. 9 of the heat transfer performance experiment, is a cross-sectional view corresponding to FIG.

【符号の説明】 DESCRIPTION OF SYMBOLS

10 伝熱管 12 プレートフィン 14 吸収液 16 外周面 18 凹部 20 凸部 22 不連続部 10 heat transfer pipe 12 plate fin 14 absorbing solution 16 outer peripheral surface 18 recess 20 projection 22 discontinuity

Claims (3)

    【特許請求の範囲】 [The claims]
  1. 【請求項1】 略鉛直方向に配管されて吸収液が管内面に沿って流下せしめられる一方、管外面に複数の冷却フィンが装着されて冷却空気が接触せしめられる空冷式の吸収器用伝熱管であって、 5〜75°のリード角で管内面を管長手方向に向かって螺旋状に延びる凹部と凸部を、管周方向で交互に位置するように、それぞれ管周方向で1.0〜5.0mmのピッチで形成すると共に、該凸部の該凹部に対する突出高さを0.2〜0.6mmとする一方、かかる凸部の表面を湾曲断面形状とし、且つ前記凹部の底部を実質的な不連続部を有する断面形状としたことを特徴とする吸収器用伝熱管。 1. A While substantially vertical direction in the piping absorption liquid is made to flow down along the inner surface, the absorption dexterous heat transfer tube of the air-cooled plurality of cooling fins on the tube outer surface is brought into contact with the cooling air is mounted there are, 1.0 to concave portions and convex portions extending toward the inner surface in the longitudinal direction of the tube in a spiral lead angle of 5 to 75 °, so as to be positioned alternately in the circumferential direction of the pipe, each pipe circumferential direction and forming a pitch of 5.0 mm, while the 0.2~0.6mm the protrusion height relative recess of the convex portion, the surface of such protrusions and curved cross-sectional shape, and substantially the bottom of the recess absorbing dexterity heat transfer tube, characterized in that the cross-sectional shape having a discontinuity portion.
  2. 【請求項2】 前記凸部が、管軸方向一方の側に傾斜して設けられている請求項1に記載の吸収器用伝熱管。 Wherein said convex portion is absorbed dexterity heat transfer tube according to claim 1 is provided to be inclined to one side in the tube axis direction.
  3. 【請求項3】 前記凹部および凸部のリード角よりも小さなリード角を有するコイル部材が、管内に挿入されて管内周面に密接されている請求項1又は2に記載の吸収器用伝熱管。 3. A coil member having a smaller lead angle than the lead angle of the concave and convex portions, the absorption dexterity heat transfer tube according to claim 1 or 2 is tightly inserted into the tube circumference to the tube.
JP9838694A 1994-05-12 1994-05-12 Absorption dexterity heat transfer tube Expired - Fee Related JP3617538B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP9838694A JP3617538B2 (en) 1994-05-12 1994-05-12 Absorption dexterity heat transfer tube

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP9838694A JP3617538B2 (en) 1994-05-12 1994-05-12 Absorption dexterity heat transfer tube

Publications (2)

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JPH07305918A true true JPH07305918A (en) 1995-11-21
JP3617538B2 JP3617538B2 (en) 2005-02-09

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5707634A (en) * 1988-10-05 1998-01-13 Pharmacia & Upjohn Company Finely divided solid crystalline powders via precipitation into an anti-solvent
EP2195586A1 (en) * 2007-10-05 2010-06-16 Muovitech AB Collector

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5707634A (en) * 1988-10-05 1998-01-13 Pharmacia & Upjohn Company Finely divided solid crystalline powders via precipitation into an anti-solvent
EP2195586A1 (en) * 2007-10-05 2010-06-16 Muovitech AB Collector
EP2195586A4 (en) * 2007-10-05 2011-02-23 Muovitech Ab Collector
US9546802B2 (en) 2007-10-05 2017-01-17 Muovitech Ab Pipe collector for heat pump systems

Also Published As

Publication number Publication date Type
JP3617538B2 (en) 2005-02-09 grant

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