WO2001092806A1 - Tube chauffant pourvu de rainures internes et echangeur de chaleur - Google Patents

Tube chauffant pourvu de rainures internes et echangeur de chaleur

Info

Publication number
WO2001092806A1
WO2001092806A1 PCT/JP2001/004595 JP0104595W WO0192806A1 WO 2001092806 A1 WO2001092806 A1 WO 2001092806A1 JP 0104595 W JP0104595 W JP 0104595W WO 0192806 A1 WO0192806 A1 WO 0192806A1
Authority
WO
WIPO (PCT)
Prior art keywords
tube
fin
heat transfer
fins
spiral
Prior art date
Application number
PCT/JP2001/004595
Other languages
English (en)
Japanese (ja)
Inventor
Seiichi Ishikawa
Kotaro Nagahara
Shunroku Sukumoda
Original Assignee
Mitsubishi Shindoh Co., Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Shindoh Co., Ltd. filed Critical Mitsubishi Shindoh Co., Ltd.
Priority to AU2001262677A priority Critical patent/AU2001262677A1/en
Publication of WO2001092806A1 publication Critical patent/WO2001092806A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element

Definitions

  • the present invention relates to a heat transfer tube with an inner groove having a spiral fin formed on the inner surface of a metal tube at a higher degree than before, and a heat exchange device using the same.
  • Background art '' This type of heat transfer tube with an inner groove is mainly used as an evaporator tube or a condenser tube in a heat exchanger of an air conditioner or a cooling device.
  • Heat transfer tubes having fins are widely commercially available.
  • Heat transfer tubes which are currently the mainstream, are passed through a seamless (seamless) tube obtained by drawing or extruding through a floating plug with a spiral groove formed on the outer peripheral surface. It is manufactured by rolling spiral fins over the entire surface.
  • the heat transfer medium liquid accumulated on the lower inside of the heat transfer tube is swept away by the steam flow to form the spiral fins. It is wound up along the entire inner surface of the pipe.
  • the entire inner peripheral surface of the pipe is almost uniformly wetted, so that a part of the inner peripheral surface of the pipe is dried.So-called dryout can be prevented, and the area of the region where boiling occurs can be increased to increase the boiling efficiency. Can be.
  • the outer diameter of the metal tube is 7 to 1 O mm
  • the pitch of the spiral fins in the direction perpendicular to the tube axis is about 0.37 mm.
  • the height of the fin from the inner peripheral surface of the metal tube is about 0.22 mm. Degrees.
  • the width of the spiral groove formed between the fins in a direction perpendicular to the tube axis is about 0.2 mm, and the angle formed by both side surfaces of the fins is about 50 °,
  • the lead angle formed by the axis is about 20 °.
  • Refrigerants such as R 125 (HF C 125), R 4 10 A (HFC 41 OA), R 32 (HFC 32), and R407C (HFC407C) have been proposed as alternative refrigerants.
  • R 125 HF C 125
  • R 4 10 A HFC 41 OA
  • R 32 HFC 32
  • R407C HFC407C
  • a first object of the present invention is to provide a heat transfer tube with an inner groove and a heat exchange device that can achieve high heat exchange efficiency even when a refrigerant having a lower viscosity than in the past is used.
  • a heat exchanger is manufactured using this type of heat transfer tube with internal grooves, a large number of heat radiating plates made of aluminum or the like are arranged in parallel, and through holes formed in these heat radiating plates are provided with internal groove grooves. After passing through the heat transfer tube, it is necessary to slightly expand the heat transfer tube with the internal groove through the expansion plug inside the heat transfer tube with the internal groove and fix it to the heat sink.
  • a second object of the present invention is to provide an inner grooved heat transfer tube which has a small fin collapse even after performing a pipe expansion operation, can maintain the fin height, and has a high heat exchange efficiency. And there.
  • Japanese Patent Application Laid-Open No. 4-260733 discloses that in a heat transfer tube with an inner surface groove having a spiral fin formed on the inner surface, a fin apex angle is set in order to prevent the fin from being collapsed at the time of expansion.
  • the fin height is 0.1-0.25 mm
  • the ratio of fin top width to fin height is 0.3-1.5
  • groove bottom width An inner grooved heat transfer tube having a diameter of 0.1 to 0.3 mm is described.
  • this heat transfer tube with internal grooves only prevents collapse by simply flattening the top of the tube, and does not focus on improving low-viscosity heat exchange performance.
  • Japanese Patent Application Laid-Open No. H08-105569 discloses that in a heat transfer tube with an inner groove formed with a spiral fin on the inner surface, the fin has an angle of 10 to 20 ° and a height of the fin of 0.
  • a heat transfer tube with an inner groove has been proposed in which the bottom width of the groove is 0.1 to 0.3 mm and the lead angle of the fin is 10 to 30 °. Even with a heat transfer tube with internal grooves, it is difficult to obtain sufficient heat exchange efficiency when using a low-viscosity refrigerant.
  • Japanese Patent Application Laid-Open No. 2-57878 / 98 proposes a heat transfer tube with a groove on the inner surface having a spiral fin formed on the inner surface; a fin having an inclined surface is proposed.
  • the slope is low and the slope is gentle, so it is difficult to obtain sufficient heat exchange efficiency when using a low-viscosity refrigerant.
  • Japanese Unexamined Patent Publication No. 7-22509 ° discloses an inner grooved heat transfer tube in which a spiral fin is formed on the inner surface, in which an inclined surface is formed at the top of the fin. Since the cross-sectional shape itself is low and the inclination angle is gentle as in the past, it is difficult to obtain sufficient heat exchange efficiency when using a low-viscosity refrigerant. Disclosure of the invention In order to solve the above problems, a heat transfer tube with an inner surface groove according to the present invention has a number of spiral fins formed on an inner peripheral surface of a metal tube, the spiral fin having a tube axis of the metal tube as a spiral axis. The pitch of the fins in the direction perpendicular to the pitch is 0.22 to 0.28 ⁇ , and the height of the fins from the inner peripheral surface of the metal pipe is 0.23 to 0.28 mm. It features that.
  • the internally grooved heat transfer tube and the heat exchanger since the density and the cross-sectional shape of the spiral fin are set as described above, even when a low-viscosity refrigerant is used, disturbance to the refrigerant is caused. The effect is sufficiently high and high heat exchange efficiency can be obtained. Also, when assembling the heat exchanger, when expanding the heat transfer tube with internal grooves through an expansion plug to fix the heat sink, the spiral fins are pushed by the expansion plug rather than collapsed by contact with the expansion plug. Incline.
  • the height of the spiral fins does not become short, so that the effect of disturbing the refrigerant is not easily reduced, and since the inner area is not easily changed before and after the pipe expansion, the heat exchange performance is hardly reduced by the pipe expansion.
  • the heat transfer tube with a surface groove according to the present invention has a high density of spiral fins, and therefore has many contact points with the mandrel, and the force from the mandrel is easily dispersed. Therefore, since uniform bending stress is applied to the inner grooved heat transfer tube, there is also an advantage that wrinkles on the outer peripheral surface of the metal tube due to imbalance in bending stress are less likely to occur.
  • the outer diameter of the metal tube is 6 to 1 O mm
  • the width of the spiral groove formed between the fins in a direction perpendicular to the tube axis is 0.1 to 0.18 mm.
  • the angle between the two sides of the fin is 0 to 20 °
  • the lead angle between the fin and the tube axis is 14 to 35 °
  • the top of the fin in a direction perpendicular to the tube axis is 0.1 to 0.3.
  • a heat exchanger is formed using the above-described grooved heat transfer tube, and a refrigerant having a lower viscosity than R 22 (HCFC 22) is circulated through the heat exchanger. It is characterized in that heat exchange is performed by causing the heat exchange. The viscosity changes with temperature and pressure, but the order of the viscosity is almost the same. According to such a heat transfer tube with an inner groove and a heat exchange device, even when a low-viscosity refrigerant is used, the heat exchange efficiency can be increased by the spiral fins formed at a high density and high.
  • FIG. 1 is an enlarged sectional view showing an embodiment of a heat transfer tube with an inner groove according to the present invention.
  • FIG. 2 is a plan view in which the inner peripheral surface of the embodiment is partially developed.
  • FIG. 3 is an enlarged cross-sectional view of the fin of the embodiment.
  • FIG. 4 is an enlarged cross-sectional view of the fin when the embodiment is subjected to a pipe expanding process.
  • FIG. 5 is an enlarged cross-sectional view of the fin when the example is subjected to a pipe expanding process.
  • FIG. 6 is a block diagram showing one embodiment of the heat exchange device of the present invention.
  • FIG. 7 is a front view showing an example of a heat exchanger used in the heat exchanger.
  • FIG. 8 is an enlarged cross-sectional view of the heat transfer tube with inner grooves according to the embodiment of the present invention.
  • FIG. 9 is an enlarged cross-sectional view of the heat transfer tube with an inner groove according to the same embodiment after expansion.
  • FIG. 10 is an enlarged cross-sectional view of the heat transfer tube with an inner surface groove according to the embodiment after being expanded.
  • FIG. 11 is a graph showing a performance difference between the example and the comparative example.
  • FIG. 12 is a block diagram of an apparatus used for performance measurement of the example and the comparative example.
  • FIG. 1 and 2 are a cross-sectional view and a part of one embodiment of an inner grooved heat transfer tube according to the present invention.
  • FIG. 3 is a plan view that is partly developed.
  • the inner grooved heat transfer tube 1 is formed of a metal having high thermal conductivity such as copper, copper alloy, aluminum, aluminum alloy, and the like.
  • a number of spiral fins 2 are formed in parallel with each other, and a spiral groove 4 is formed between the spiral fins 2.
  • a welded portion 6 that rises from the inner surface of the metal tube and extends in the tube axis direction is formed in a part of the inner surface of the heat transfer tube 1 with the inner surface groove in the circumferential direction.
  • Each part 8 is formed.
  • 6A shown in FIG. 2 is a welding surface.
  • the heat transfer tube with an inner groove is applicable not only to such a welded tube (electrode tube) but also to a seamless tube. In that case, the welded portion 6 and the finless portion 8 do not exist. In the case of a seamless pipe, it is necessary to use a floating plug to form the fin 2, and in the case of using a floating plug, a thin and high fin as described below is actually used. It is difficult to form 2 at high density.
  • FIG. 3 is an enlarged sectional view of a part of FIG.
  • the outer peripheral surface of the inner grooved heat transfer tube 1 is represented by a straight line, but it is needless to say that the outer peripheral surface is a curved surface having a constant curvature.
  • a first feature of the present invention resides in that the pitch P of the fin 2 in the direction orthogonal to the tube axis is set to 0.22 to 0.28 mm.
  • This dimension is considerably smaller than the fin pitch of 0.37 mm for the internally grooved heat transfer tube that was conventionally used industrially, and it was not only industrially difficult to manufacture, but also It was thought that if the pitch was set to a very narrow pitch, the spiral fins 2 would be too thin, and the spiral fins 2 would be severely crushed during pipe expansion, and would not be industrially usable.
  • the present inventors formed such thin and high fins at a high density by combining roll rolling and electrode tube processing instead of seamless pipes, and by further optimally setting the rolling conditions.
  • the present inventors have found that even when such thin and high fins are formed, it is found that the fins are hardly crushed by the expanding process, and have completed the present invention.
  • the pitch P of the fins 2 in the direction perpendicular to the tube axis is more preferably 0.25 to 0.27 mm. In that case, the balance between the ease of manufacture and the effects of the present invention is good.
  • a second feature of the present invention resides in that the height H of the fin from the inner peripheral surface of the metal tube is 0.23 to 0.28 mm.
  • the range of the fin height H is higher in comparison with the fin pitch P described above, as it is clearly different from the conventional one.
  • the fin height H is more preferably 0.24 to 0.26 mm, and the ratio H / P between the fin height H and the fin pitch P is preferably 0.9 to 1.1. Within these ranges, the balance between the manufacturing performance and the performance of the heat transfer tube with inner groove 1 is good.
  • the outer diameter of the inner grooved heat transfer tube 1 is not limited, but generally, the outer diameter of the inner grooved heat transfer tube 1 is 6 to 1 Omm. If the outer diameter of the inner grooved heat transfer tube 1 is too large or small, the effect of the present invention may be relatively reduced.
  • the dimensions of the spiral fins 2 can be made larger in advance by the reciprocal of the diameter reduction ratio.
  • the thickness of the heat transfer tube 1 with the inner groove is not limited, but is generally used. The thickness may be in accordance with the typical thickness of the heat transfer tube, and may be, for example, about 0.2 to 0.5 mm.
  • the width W1 of the spiral groove 4 in the direction orthogonal to the tube axis is preferably 0.1 to 0.18 mm, and more preferably 0.12 to 0.16 mm. . Within such a range, the effects of the present invention can be enhanced. The same applies to the other dimensions below, but if the boundary where the two surfaces intersect is chamfered, the intersection line of each virtual extension surface of the two surfaces is Standard.
  • the cross-sectional shape of the spiral fin 2 is a trapezoidal shape in which the crown 2C is inclined, and the angle formed by both side surfaces 2A and 2B is 0 to 20 °, more preferably 5 to 15 °.
  • This angle] 3 is considerably smaller than the fin used in conventional realistic heat transfer tubes with internal grooves, and the side surfaces 2A and 2B of the spiral fin 2 stand up against the inner surface of the metal tube. It can be said that there is.
  • the viscosity of the refrigerant is small, even if such a steep spiral fin 2 is formed, the adverse effect of increasing the pressure loss of the refrigerant flowing through the heat transfer tube 1 with the inner surface groove is small, and the disturbance effect is large. It is useful in obtaining the effects of the invention.
  • the lead angle ⁇ between the spiral fin 2 and the tube axis is not limited in the present invention, but is preferably 14 to 35 °, more preferably 14 to 30 °. Within this range, a good disturbance effect can be obtained without increasing the pressure loss of the refrigerant, and the heat exchange performance can be improved.
  • the value W 3 ZH obtained by dividing the width W 3 of the crown 2 C of the spiral fin 2 in the direction perpendicular to the pipe axis by the fin height ⁇ is preferably 0.1 to 0.3, and more preferably 0 to 0.3. 0.22 to 0.28. Within this range, the top portion 2C of the spiral fin 2 is less crushed even when the tube is expanded, the spiral fin 2 falls down and escapes, and the height of the spiral fin 2 is easily maintained even when the tube is expanded. .
  • FIG. 6 shows an embodiment of the heat exchange device according to the present invention.
  • This device has a compressor 10 for pressurizing a refrigerant, and the pressurized refrigerant radiates heat to the outside through a condensing-side heat exchanger 12 and is liquefied in a liquid receiver 16. Is stored.
  • the liquefied refrigerant in the liquid receiving part 16 passes through an expansion valve 18 consisting of a capillary tube and the like, and its pressure is reduced.In the vaporized state, the refrigerant passes through the evaporating heat exchanger 14 and absorbs heat from the outside. , And is pressurized again by the compressor 10.
  • the heat transfer tube with an inner surface groove 1 of the present invention is used at least in a part of the condensing-side heat exchanger 12 and the evaporating-side heat exchanger 14.
  • FIG. 7 shows an example of the evaporator-side heat exchanger 14 and the condensing-side heat exchanger 12.
  • the heat exchanger has a number of radiating plates 20 arranged in parallel and a state penetrating through the radiating plates 20. And a number of internally grooved heat transfer tubes 1 secured in the above manner.
  • the heat transfer tube with inner groove 1 in this example is bent into U-shaped tubes having a semicircular portion 1 mm at one end, and after these U-shaped tubes 1 are fixed through the heat sink 20, each U-shaped tube is fixed.
  • the heat radiating plate 20 is generally a thin aluminum plate, which has holes formed in advance, through which straight portions of the U-tube 1 are respectively passed. The plug is press-fitted over the entire length of each straight portion, whereby the straight portion is expanded, and the outer peripheral surface of the heat transfer tube 1 with the inner groove is tightly fixed to the heat sink 20.
  • the refrigerant is first sent into the inner grooved heat transfer tube 1 located at the substantially central portion through the introduction tube 26, and this refrigerant is branched into two branches by the branch tube 24, and the refrigerant is divided into upper and lower portions of the heat exchanger. , And further discharged through the outlet pipe 28.
  • the heat medium branches and flows from the center of the heat exchanger to both ends, good heat exchange efficiency can be obtained when a fan that blows air around the center of the heat exchanger is provided. Can be .
  • the expansion plug When the heat exchangers 12 and 14 are set up, the expansion plug is pressed into the inner grooved heat transfer tube 1. At this time, the expansion plug is formed on the inner surface of the inner grooved heat transfer tube 1.
  • the helical fin 2 is inclined to the downstream side in the press-fitting direction due to contact with the tube-expanding plug, and is hardly collapsed. This is because the difference between the thickness at the leading end and the thickness at the lower end is smaller because the spiral fin 2 of the present invention is thin and high and has a small apex angle.
  • the spiral fins 2 are less likely to be crushed by the expanding process, and the height thereof can be maintained, so that not only a large contact area between the spiral fins 2 and the refrigerant can be ensured, but also good disturbance to the refrigerant.
  • the effect can be obtained, and the effect of the present invention can be obtained.
  • the spiral fin 2 of the present invention is a rolling fin having a spiral groove for fin rolling formed on the outer peripheral surface while continuously running a long flat metal plate strip. The spiral fin 2 is rolled by rolling. At this time, if the material does not penetrate deep into the spiral grooves for rolling the individual fins and the material does not penetrate halfway, the rolling of the rolling rolls causes the rolling as shown in Fig. 3. On the downstream side in the direction, the tip surface 2C tends to be slightly higher than the inner wall surface of the pipe.
  • the most significant effect of the present invention is when a refrigerant having a viscosity lower than that of R22 (HCFC 22) is used. It is. Specifically, the value at the pressure at which the saturation temperature on the liquid side becomes 2 ° C is less than 218.2 ⁇ Pas, more preferably 210 ⁇ Pas or less. . Table 1 below shows the relationship between the type of refrigerant and the viscosity, density, and kinematic viscosity at a pressure at which the liquid-side saturation temperature becomes 2 ° C. table 1
  • R125 HFC125
  • R32 HFC32
  • R410A HFC41OA
  • R407C HFC407C
  • R410A is a mixed refrigerant in which R32 and R125 are mixed at 50%: 50%.
  • R407A is a mixed refrigerant obtained by mixing R32, R125, and R134A in a ratio of 23%: 25%: 52%.
  • insufficient disturbance by the spiral fin not only reduces the heat exchange efficiency, but also Although the separation is likely to occur every time, according to the present invention, such a problem can be prevented.
  • the viscosity of the R 2 2 (HCFC 2 2) Even when a refrigerant having a low viscosity is used, the effect of disturbing the refrigerant is sufficiently high, and high heat exchange efficiency can be obtained.
  • the spiral fins 2 are less likely to collapse due to contact with the expansion plug, and are pushed by the expansion plug to be inclined. I do. As a result, the height of the spiral fins 2 does not become short, so that the effect of disturbing the refrigerant is not easily reduced, and since the inner area is hardly changed before and after the pipe expansion, the heat exchange performance is not likely to be reduced by the pipe expansion.
  • the heat transfer tube with an inner groove has a high density of spiral fins 2 so that there are many points of contact with the mandrel, and the force from the mandrel is dispersed. Easy to be. Therefore, since a uniform bending stress is applied to the heat transfer tube with the inner groove, there is also an advantage that wrinkles on the outer peripheral surface of the metal tube due to the imbalance of the bending stress are less likely to occur.
  • the cross-sectional shape of the inner grooved heat transfer tube 1 is not limited to a circular shape, and may be an elliptical cross-sectional shape or a flat tubular shape, if necessary.
  • a working fluid such as pure water, alcohol, chlorofluorocarbon, or a mixed solvent may be sealed under reduced pressure in the heat transfer tube 1 with an inner groove, and both ends of the tube may be closed to be used as a heat pipe.
  • a fin is formed by rolling a metal plate strip made of phosphorus-deoxidized copper with a fin rolling roll, and the plate strip is subjected to an electric resistance welding process to form a heat transfer tube with an inner surface groove having the following dimensions. Manufactured.
  • FIG. 8 shows a micrograph of the cross section enlarged. As shown in FIG. 8, it can be seen that a thin and tall spiral fin, clearly different from the conventional product, is formed at a high density.
  • Figs. 9 and 10 corresponds to the case where the expansion plug was pressed in from the side where the slope (2C) at the top of the fin was higher, and it can be seen that the spiral fin was inclined while curving in a curved shape.
  • Fig. 10 corresponds to the case where the expansion plug is press-fitted from the side where the slope (2C) is lowered. In each case, the top of the spiral fin 2 was hardly crushed, indicating that the height of the spiral fin 2 did not decrease. This is an effect not known conventionally.
  • Lead angle between fin and tube axis 16 °
  • the test device used was the one shown in Fig. 12, and the experimental conditions were as follows.
  • the types of refrigerant used are R22, R410A, and R407C. Table 2
  • U-tubes were manufactured by bending 100 heat-transfer tubes each having a square groove in the experimental example and the comparative example, and whether or not wrinkles occurred on the outer peripheral surface of the U-shaped processed portion was inspected.
  • the outer diameter of the mandrel for hairpin processing was 0.25 mm smaller than the inner diameter of the heat transfer tube with internal grooves.
  • channel with this invention, and a heat exchange apparatus have sufficiently high disturbance effect with respect to a refrigerant

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention concerne un tube chauffant pourvu de rainures internes. Un certain nombre d'ailettes en spirale (2) sont formées sur la surface périphérique interne d'un tube métallique (1), autour de son axe. Le pas (P) des ailettes (2) dans une direction perpendiculaire à l'axe du tube est compris entre 0,22 et 0,28 mm. La hauteur (H) des ailettes (2) à partir de la surface périphérique interne du tube métallique est comprise entre 0,23 et 0,28 mm. Le diamètre externe du tube métallique (1) est compris entre 6 et 10 mm. La largeur de fond (W1) d'une rainure en spirale (4) dans une direction perpendiculaire à l'axe du tube est comprise entre 0,1 et 0,18 mm. L'angle (β) formé par les deux faces des ailettes est compris entre 0 et 20°. L'angle d'attaque (α) formé par les ailettes et l'axe du tube est compris entre 14 et 35°. La valeur obtenue en divisant la largeur (W3) des ailettes au niveau de la partie supérieure dans une direction perpendiculaire à l'axe du tube par la hauteur (H) des ailettes est comprise entre 0,1 et 0,3.
PCT/JP2001/004595 2000-05-31 2001-05-31 Tube chauffant pourvu de rainures internes et echangeur de chaleur WO2001092806A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2001262677A AU2001262677A1 (en) 2000-05-31 2001-05-31 Heating tube with internal grooves and heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2000-163611 2000-05-31
JP2000163611A JP2001343194A (ja) 2000-05-31 2000-05-31 内面溝付伝熱管および熱交換装置

Publications (1)

Publication Number Publication Date
WO2001092806A1 true WO2001092806A1 (fr) 2001-12-06

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AU (1) AU2001262677A1 (fr)
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2668460A1 (fr) * 2011-01-28 2013-12-04 Carrier Corporation Structures de tuyau destinées à un échangeur de chaleur
US11774179B2 (en) 2017-06-22 2023-10-03 Rheem Manufacturing Company Heat exchanger tubes and tube assembly configurations

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4925597B2 (ja) * 2005-03-28 2012-04-25 株式会社コベルコ マテリアル銅管 ヒートパイプ用伝熱管及びヒートパイプ
JP2013092335A (ja) * 2011-10-27 2013-05-16 Mitsubishi Alum Co Ltd 熱交換器用アルミニウム細管およびこれを用いた熱交換器

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Publication number Priority date Publication date Assignee Title
JPS62142995A (ja) * 1985-12-17 1987-06-26 Hitachi Cable Ltd 内面らせん溝付伝熱管
JPH04260793A (ja) * 1991-02-13 1992-09-16 Furukawa Electric Co Ltd:The 内面溝付伝熱管
JPH04327792A (ja) * 1991-04-25 1992-11-17 Sumitomo Light Metal Ind Ltd 内面溝付銅管
JPH085278A (ja) * 1994-06-20 1996-01-12 Mitsubishi Shindoh Co Ltd 内面溝付伝熱管
JPH08105699A (ja) * 1994-10-03 1996-04-23 Hitachi Cable Ltd 内面溝付伝熱管
JPH08327272A (ja) * 1995-05-31 1996-12-13 Mitsubishi Heavy Ind Ltd 伝熱管及びその製造方法
JPH0926280A (ja) * 1995-07-12 1997-01-28 Sanyo Electric Co Ltd 内面溝付冷媒配管

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62142995A (ja) * 1985-12-17 1987-06-26 Hitachi Cable Ltd 内面らせん溝付伝熱管
JPH04260793A (ja) * 1991-02-13 1992-09-16 Furukawa Electric Co Ltd:The 内面溝付伝熱管
JPH04327792A (ja) * 1991-04-25 1992-11-17 Sumitomo Light Metal Ind Ltd 内面溝付銅管
JPH085278A (ja) * 1994-06-20 1996-01-12 Mitsubishi Shindoh Co Ltd 内面溝付伝熱管
JPH08105699A (ja) * 1994-10-03 1996-04-23 Hitachi Cable Ltd 内面溝付伝熱管
JPH08327272A (ja) * 1995-05-31 1996-12-13 Mitsubishi Heavy Ind Ltd 伝熱管及びその製造方法
JPH0926280A (ja) * 1995-07-12 1997-01-28 Sanyo Electric Co Ltd 内面溝付冷媒配管

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2668460A1 (fr) * 2011-01-28 2013-12-04 Carrier Corporation Structures de tuyau destinées à un échangeur de chaleur
US11774179B2 (en) 2017-06-22 2023-10-03 Rheem Manufacturing Company Heat exchanger tubes and tube assembly configurations

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JP2001343194A (ja) 2001-12-14
AU2001262677A1 (en) 2001-12-11

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