EP1087198A1 - Wärmeaustauschsrohr mit inneren nuten und verfahren zu deren herstellung - Google Patents

Wärmeaustauschsrohr mit inneren nuten und verfahren zu deren herstellung Download PDF

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Publication number
EP1087198A1
EP1087198A1 EP00915441A EP00915441A EP1087198A1 EP 1087198 A1 EP1087198 A1 EP 1087198A1 EP 00915441 A EP00915441 A EP 00915441A EP 00915441 A EP00915441 A EP 00915441A EP 1087198 A1 EP1087198 A1 EP 1087198A1
Authority
EP
European Patent Office
Prior art keywords
grooves
heat
transfer pipe
pipe
rows
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP00915441A
Other languages
English (en)
French (fr)
Other versions
EP1087198A4 (de
Inventor
Hirokazu Fujino
Kazushige Kasai
Kanji Akai
Noriaki Okamoto
Masaru Uchimitsu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries 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 Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP1087198A1 publication Critical patent/EP1087198A1/de
Publication of EP1087198A4 publication Critical patent/EP1087198A4/de
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C37/00—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
    • B21C37/06—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape of tubes or metal hoses; Combined procedures for making tubes, e.g. for making multi-wall tubes
    • B21C37/15—Making tubes of special shape; Making tube fittings
    • B21C37/20—Making helical or similar guides in or on tubes without removing material, e.g. by drawing same over mandrels, by pushing same through dies ; Making tubes with angled walls, ribbed tubes and tubes with decorated walls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C37/00—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
    • B21C37/06—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape of tubes or metal hoses; Combined procedures for making tubes, e.g. for making multi-wall tubes
    • B21C37/08—Making tubes with welded or soldered seams
    • 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 structure of a heat-transfer pipe with internal grooves having grooves in an inner surface of a pipe body.
  • a heat-transfer pipe in a heat exchanger such as an evaporator, a condenser or the like for an air conditioner is conventionally provided with spiral grooves in an inner surface of the pipe from a viewpoint of improvement in its heat transfer efficiency as shown in Japanese Patent Laid-Open Publication No. Hei 9-42881 so that a heat-transfer area is enlarged and an agitation effect is improved by allowing a refrigerant flowing in the pipe to annularly flow.
  • the inner surface of the pipe is divided into a plurality of areas in the circumferential direction, each having a plurality of rows of grooves arranged in V-shaped patterns, for example, which are symmetric with respect to the direction of a pipe axis and have equal widths in the circumferential direction, for example, as shown in Japanese Patent Laid-Open Publication No. Hei 9-42880.
  • the distribution of the refrigerant flowing in the pipe in the pipe circumferential direction can be made ununiform because of flow merging and dividing actions by the plurality of the grooves arranged in V-shaped patterns provided in the inner surface of the pipe which are symmetric with respect to the pipe axis direction and have equal widths in the circumferential direction as compared with the aforementioned heat-transfer pipe having the spiral grooves. Since high heat transfer efficiency is achieved in areas where the liquid refrigerant becomes a thin film as a result, the heat transfer efficiency at the time of condensation is improved.
  • An object of the present invention is to provide a heat-transfer pipe with internal grooves having a heat transfer performance improved as much as possible by reducing a pressure loss and appropriately controlling refrigerant flows in the pipe to be even when a refrigerant flow rate is low, and a manufacturing method thereof as well as a manufacturing device, by which the above-described problems can be solved.
  • each aspect of the present invention has the following means for solving the problems.
  • a plurality of rows of grooves arranged in V-shaped patterns 3 symmetric with respect to a pipe axis direction are provided on an inner surface 2 of a pipe body 1a; and widths of the plurality of rows of the grooves 3 arranged in the V-shaped patterns are made unequal in a circumferential direction.
  • secondary grooves 6 having a prescribed depth are formed from a top 5a side towards a base 5b side at least in part of projected portions 5 formed between respective grooves 3 of the plurality of rows of the grooves 3 arranged in the V-shaped patterns.
  • the secondary grooves 6 having a prescribed depth are formed from the top part 5a side towards the bottom part 5b side at least in part of the projected portions 5 formed between the respective grooves 3 of the plurality of rows of the grooves 3 arranged in V-shaped patterns, the flow resistance of the refrigerant flowing in the pipe is further reduced by the secondary grooves 6 and thereby a heat transfer performance is effectively improved even when a refrigerant flow rate is low.
  • the secondary grooves 6 are notched grooves in a spiral direction.
  • the flow resistance of the refrigerant flowing in the pipe is effectively reduced by the secondary grooves 6 composed of the notched grooves in the spiral direction. Further, a swirling force is increased in the spiral direction and thereby the heat transfer performance is improved.
  • secondary grooves 7 having a prescribed depth are formed in an outer surface of at least part of projected portions 5 formed between respective grooves 3 of the rows of grooves 3 arranged in the V-shaped patterns.
  • the secondary grooves 7 are fine grooves extending from one side surface of the projected portions 5 to the other side surface thereof.
  • the flow resistance of the refrigerant flowing in the pipe is effectively reduced by the secondary grooves 7 composed of fine grooves extending from one side surface to the other side surface of the projected portions 5 in this case, and therefore the heat transfer performance is improved. Also, even when the pipe is expanded, both sides of the fine grooves are not crushed and thereby the heat-transfer performance is not deteriorated.
  • a second marking roll 12 for marking secondary grooves 7 at least in part of projected portions 5 formed between respective grooves 3 of the plurality of rows of the grooves 3 arranged in the V-shaped patterns and a roll forming device 17 for forming the flat plate-like heat-transfer pipe material 13 into a cylindrical pipe are used to continuously mark the plurality of rows of the grooves 3 arranged in the V-shaped patterns and the secondary grooves 7 in the flat plate-like heat-transfer pipe material 13 successively by the first and second marking rolls 11, 12 and then form a cylindrical pipe by roll forming by the roll forming device 17.
  • the heat-transfer pipe with internal grooves having the constitutions of the first, fourth and fifth aspects can be easily manufactured only by combining the above-described first and second marking rolls 11, 12 in the direction of the movement of the flat plate-like heat-transfer pipe material 13 to perform continuous markings successively in two stages.
  • a second marking roll 12 for marking secondary grooves 7 at least in part of projected portions 5 formed between respective grooves 3 of the plurality of rows of the grooves 3 arranged in V-shaped patterns and a roll forming device 17 for forming the flat plate-like heat-transfer pipe material 13 into a cylindrical pipe are provided successively side by side in a direction of movement of the flat plate-like heat-transfer pipe material 13 to continuously mark the grooves 3 arranged in the V-shaped patterns and the secondary grooves 7 successively by the first and second marking rolls 11, 12 and then form a cylindrical pipe by roll forming by the roll forming device 17.
  • the heat-transfer pipe with internal grooves having the constitutions of the first, fourth and fifth aspects can be easily manufactured only by combining the above-described first and second marking rolls 11, 12 in the direction of the movement of the flat plate-like heat-transfer pipe material 13 to perform markings successively in two stages.
  • Figs. 1 to 3 show a structure of a heat-transfer pipe with internal grooves according to a first embodiment of the present invention.
  • first to fifth groups A - E of a plurality of rows of grooves is provided on an inner surface 2 of a pipe body 1a having an electric welded pipe structure.
  • Those groups of grooves are comprised of grooves 3 which are arranged to be symmetric, with respect to a pipe axis direction and to form relatively sharp V-shape patterns, and which are arranged with width of the grooves unequal to each other in the circumferential direction and with a lead angle ⁇ of the grooves different from each other, so as to promote a turbulent flow of a refrigerant liquid flowing in the pipe body 1a and to promote the refrigerant liquid to become a thin film because coarse and minute refrigerant liquid portions are formed by dividing and merging the refrigerant liquid flow.
  • reference numeral 5 denotes a projected portion formed between the respective grooves 3 arranged in V-shaped patterns.
  • Reference numerals 5a and 5b denote a top and a base of the projected portion, respectively.
  • the first to fifth groups A - E composed of rows of grooves, which are arranged in V-shaped patterns and have a lead angle ⁇ different in next groups, are provided side by side with unequal widths in the circumferential direction, the refrigerant liquid flows ununiformly in the circumferential direction to swirl while repeatedly dividing and merging at edge portions of V-shape patterns of the respective grooves 3. Consequently, the grooves of the present invention can obtain an annular flow close to the one conventionally obtained by combination of spiral grooves even though the grooves arranged in V-shaped patterns are used. Thus, an effective agitation effect is achieved and thereby a heat transfer performance is improved.
  • Respective grooves 3 in the first to fifth groups A - E are formed with a prescribed lead angle ⁇ , a prescribed depth H and a prescribed number of grooves N so that the flow resistance of each groove portion is made as small as possible to reduce the pressure loss. Therefore, even when the heat-transfer pipe of the present invention is used for an evaporator at a low refrigerant flow rate, the pressure loss is reduced and thereby the heat transfer performance is improved.
  • widths of groups A - E composed of rows of grooves 3, which are arranged in V-shaped patterns and have a lead angle ⁇ different from each other, are set unequal in the circumferential direction rather than equal. Therefore, the refrigerant in the pipe has swirling flow as in the case of the conventional pipe with spiral grooves. Consequently, the heat transfer promotion effect is not deteriorated even when a refrigerant flow rate is low because the refrigerant is effectively supplied in the circumferential direction of the pipe.
  • the lead angle ⁇ , the groove depth H and the groove number N of the grooves 3 formed in the V-shaped patterns, the first to fifth groups A - E of which are arranged in the inner surface of the pile, are set to the values by which the smallest flow resistance is obtained corresponding to the aforementioned experiment results. Therefore, since the flow resistance can be made as small as possible to reduce the pressure loss as a result, a heat-transfer pipe for a heat exchanger having a sufficiently high performance can be obtained.
  • Figs. 4 to 6 show a structure of a heat-transfer pipe with internal grooves according to a second embodiment of the present invention.
  • first to fifth groups A - E of a plurality of rows of grooves is provided on an inner surface 2 of a pipe body 1a having the same electric welded pipe structure as described above.
  • Those groups of grooves are comprised of grooves 3 which are arranged to be symmetric with respect to a pipe axis direction and to form relatively sharp V-shape patterns, and which are arranged with width of the grooves unequal to each other in the circumferential direction and with a lead angle ⁇ of the grooves different from each other, so as to promote a turbulent flow of a refrigerant liquid flowing in the pipe body 1a and to promote the refrigerant liquid to become a thin film because coarse and minute refrigerant liquid portions are formed by dividing and merging the refrigerant liquid flow.
  • reference numeral 5 denotes a projected portion formed between the respective grooves 3 arranged in V-shaped patterns.
  • Reference numerals 5a and 5b denote a top and a base of the projected portion 5, respectively.
  • secondary grooves 6 are provided and the secondary grooves 6 are composed of notched grooves (chipped grooves) in the spiral direction with a prescribed depth d from the top 5a towards the base 5b. Consequently, the flow resistance of the refrigerant is reduced and the refrigerant is further urged in the swirling direction.
  • the first to fifth groups A - E composed of rows of grooves, which are arranged in V-shaped patterns and have a lead angle ⁇ different in next groups, are provided side by side with unequal widths in the circumferential direction, the refrigerant liquid flows ununiformly in the circumferential direction to swirl while repeatedly dividing and merging at edge portions of V-shape patterns of the respective grooves 3. Consequently, the grooves of the present invention can obtain an annular flow close to the one conventionally obtained by combination of spiral grooves even though the grooves arranged in V-shaped patterns are used. Thus, an effective agitation effect is achieved and thereby a heat transfer performance is improved.
  • Respective grooves 3 in the first to fifth groups A - E are formed with the secondary grooves 6 composed of notched grooves (chipped grooves) in the spiral direction as described above as well as a prescribed lead angle ⁇ , a prescribed depth H and a prescribed number of grooves as in the first embodiment, so that the flow resistance of each groove portion is made as small as possible to reduce the pressure loss. Therefore, even when the heat-transfer pipe of the present invention is used for an evaporator at a low refrigerant flow rate, the pressure loss is reduced and thereby the heat transfer performance is improved.
  • widths of groups A - E composed of rows of grooves 3, which are arranged in V-shaped patterns and have a lead angle ⁇ different from each other, are set unequal in the circumferential direction. Therefore, the refrigerant in the pipe has swirling flow as in the case of the conventional pipe with spiral grooves. Consequently, the heat transfer promotion effect is not deteriorated even when a refrigerant flow rate is low because the refrigerant is effectively supplied in the circumferential direction of the pipe.
  • the lead angle ⁇ , the groove depth H and the groove number N of the grooves 3 formed in the V-shaped patterns, the first to fifth groups A - E of which are arranged in the inner surface of the pile, are set to the values by which the smallest flow resistance is obtained.
  • the secondary grooves 6 are formed in the projected portions 5 provided between the respective grooves 3 as main grooves in V-shaped patterns and the secondary grooves 6 are notched grooves from the top 5a towards the base 5b of the projected portions 5 and are directed in the spiral direction. Therefore, since the flow resistance can be made as small as possible to reduce the pressure loss and swirling force in the spiral direction can be further increased, a heat-transfer pipe for a heat exchanger having a still higher performance can be obtained.
  • Figs. 7 to 9 show a structure of a heat-transfer pipe with internal grooves according to a third embodiment of the present invention and a constitution of a manufacturing device employing a method for manufacturing the heat-transfer pipe, respectively.
  • first to fifth groups A - E of a plurality of rows of grooves is provided on an inner surface 2 of a pipe body 1a having the same electric welded pipe structure as described above.
  • Those groups of grooves are comprised of grooves 3 which are arranged to be symmetric with respect to a pipe axis direction and to form relatively sharp V-shape patterns, and which are arranged with width of the grooves unequal to each other in the circumferential direction and with a lead angle ⁇ of the grooves different from each other, so as to promote a turbulent flow of a refrigerant liquid flowing in the pipe body 1a and to promote the refrigerant liquid to become a thin film because coarse and minute refrigerant liquid portions are formed by dividing and merging the refrigerant liquid flow.
  • reference numeral 5 denotes a projected portion formed between the respective grooves 3 arranged in V-shaped patterns.
  • Reference numerals 5a and 5b denote a top and a base of the projected portion 5, respectively.
  • secondary grooves 7 composed of fine grooves having a prescribed depth are formed from one side of an outer surface of the projected portion 5 to the other side thereof to direct toward, for example, the spiral direction. Consequently, the flow resistance of the refrigerant is reduced and the refrigerant is further urged in the swirling direction.
  • the first to fifth groups A - E composed of rows of grooves, which are arranged in V-shaped patterns and have a lead angle ⁇ different in next groups, are provided side by side with unequal widths in the circumferential direction, the refrigerant liquid flows ununiformly in the circumferential direction to swirl while repeatedly dividing and merging at edge portions of V-shape patterns of the respective grooves 3. Consequently, the grooves of the present invention can obtain an annular flow close to the one conventionally obtained by combination of spiral grooves even though the grooves arranged in V-shaped patterns are used. Thus, an effective agitation effect is achieved and thereby a heat transfer performance is improved.
  • Respective grooves 3 in the first to fifth groups A - E are formed with the secondary fine grooves 7 formed from one side of an outer surface of the projected portion 5 to the other side thereof in a prescribed depth to direct toward the spiral direction as well as with a prescribed lead angle ⁇ , a prescribed depth H and a prescribed number of grooves as in the first embodiment. Consequently, the flow resistance of each groove portion is made as small as possible to reduce the pressure loss. Therefore, even when the heat-transfer pipe of the present invention is used for an evaporator at a low refrigerant flow rate, the pressure loss is reduced and thereby the heat transfer performance is improved. Also, even when the pipe is expanded, the fine grooves on the side portions are not crushed and thereby the heat transfer performance is not deteriorated.
  • widths of groups A - E composed of rows of grooves 3, which are arranged in V-shaped patterns and have a lead angle ⁇ different from each other, are set unequal. Therefore, the refrigerant in the pipe has swirling flow as in the case of the conventional pipe with spiral grooves. Consequently, the heat transfer promotion effect is not deteriorated even when a refrigerant flow rate is low because the refrigerant is effectively supplied in the circumferential direction of the pipe.
  • the lead angle ⁇ , the groove depth H and the groove number N of the grooves 3 formed in the V-shaped patterns, the first to fifth groups A - E of which are arranged in the inner surface of the pile, are set to the values by which the smallest flow resistance is obtained.
  • the secondary grooves 7 composed of fine grooves are formed from one side of an outer surface of the projected portion 5 to the other side thereof to direct toward, for example, the spiral direction. Therefore, since the flow resistance can be made as small as possible to reduce the pressure loss and swirling force in the spiral direction can be further increased, a heat-transfer pipe for a heat exchanger having a still higher performance can be obtained. Also, even when the pipe is expanded, the fine grooves on the side portions are not crushed and thereby the heat transfer performance is not deteriorated.
  • the heat-transfer pipe with internal grooves having the groups A - E of rows of the grooves arranged in V-shaped patterns and secondary grooves 7 described above are easily manufactured by the following method by using, for example, a manufacturing device shown in Fig. 9.
  • reference numeral 11 denotes a first marking roll which has a marking processing surface 11a corresponding to the first to fifth groups A - E of rows of grooves arranged as main grooves in V-shaped patterns.
  • Reference numeral 12 denotes a second marking roll which has a marking processing surface 12a for marking the fine grooves 7 provided to extend, for example, in the spiral direction from one side to the other side of an outer surface of the projected portion 5 formed between the grooves 3 arranged in V-shaped patterns in the first to fifth groups A - E.
  • Reference numeral 13 denotes a flat plate-like heat-transfer pipe material.
  • Reference numeral 16 denotes a heating device for heating and softening the heat-transfer pipe material at the time of roll forming.
  • Reference numeral 14 denotes a first pressure roller for sandwiching and pressing the flat plate-like heat-transfer pipe material 13 with the aforementioned first marking roll 11.
  • Reference numeral 15 denotes a second pressure roller for sandwiching and pressing the flat plate-like heat-transfer pipe material 13 with the aforementioned second marking roll 12.
  • Reference numeral 17 denotes a roll forming device having a roll forming hole 17a for roll-forming into a cylindrical shape the heat-transfer pipe material 13 which has the first to fifth groups A - E of rows of grooves arranged in V-shaped patterns and the secondary grooves 7 formed thereon via the first and second marking rollers 11, 12 and is heated and softened by the heating device 16.
  • the first marking roll 11 and the first pressure roller 14, the second marking roll 12 and the second pressure roller 15, the heating device 16 and the roll forming device 17 are successively provided side by side at predetermined intervals in the movement direction (see the arrow) of the heat-transfer pipe material 13.
  • the first marking roll 11 and the first pressure roller 14 are used for marking the first to fifth groups A - E of rows of grooves arranged in V-shaped patterns
  • the second marking roll 12 and the second pressure roller 15 are used for marking the secondary grooves 7 in part of the projected portions formed between the respective grooves 3 of the first to fifth groups A - E of rows of grooves arranged in V-shaped patterns
  • the heating device 16 and the roll forming device 17 are used for forming the flat plate-like heat-transfer pipe material 13 into a cylindrical pipe.
  • the first and second marking rolls 11, 12 are rotatably operated so that the respective grooves 3 of the first to fifth groups A - E and the secondary grooves 7 are successively marked in two stages on the flat plate-like heat-transfer pipe material 13, and then the heat-transfer pipe material 13 can be heated and softened by the heating device 16 and then roll-formed by the roll forming device 17 to form a cylindrical pipe.
  • the heat-transfer pipe with internal grooves having a constitution shown in Figs. 7 and 8 can be easily manufactured only by two stage successive marking of the grooves with the above-described first and second marking rolls 11, 12 combined in the direction of the movement of the flat plate-like heat-transfer pipe material 13.
  • the heat-transfer pipe with internal grooves and the manufacturing method thereof and the manufacturing device according to the present invention are useful for a heat-transfer pipe of a heat exchanger and particularly suitable for a heat-transfer pipe used for an evaporator or a condenser in an air-conditioner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP00915441A 1999-04-08 2000-04-10 Wärmeaustauschsrohr mit inneren nuten und verfahren zu deren herstellung Withdrawn EP1087198A4 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP10076799 1999-04-08
JP10076799A JP3296325B2 (ja) 1999-04-08 1999-04-08 内面溝付伝熱管
PCT/JP2000/002300 WO2000062001A1 (fr) 1999-04-08 2000-04-10 Tube de transfert thermique avec rainures internes et son procede de fabrication

Publications (2)

Publication Number Publication Date
EP1087198A1 true EP1087198A1 (de) 2001-03-28
EP1087198A4 EP1087198A4 (de) 2005-04-27

Family

ID=14282656

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00915441A Withdrawn EP1087198A4 (de) 1999-04-08 2000-04-10 Wärmeaustauschsrohr mit inneren nuten und verfahren zu deren herstellung

Country Status (5)

Country Link
EP (1) EP1087198A4 (de)
JP (1) JP3296325B2 (de)
CN (1) CN1313947A (de)
AU (1) AU746338B2 (de)
WO (1) WO2000062001A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1342971A2 (de) * 2002-03-07 2003-09-10 Wieland-Werke AG Wärmeaustauschrohr mit berippter Innenoberfläche
EP1852669A1 (de) * 2006-05-02 2007-11-07 Samsung Gwangju Electronics Co., Ltd. Wärmetauscher für einen Kühlschrank und Verfahren zur Herstellung eines Rohres dafür

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2645040B1 (de) * 2012-03-28 2017-06-21 ABB Research Ltd. Wärmetauscher für Traktionsstromrichter
CN104708292A (zh) * 2015-03-02 2015-06-17 金龙精密铜管集团股份有限公司 传热管的加工方法
CN104949564A (zh) * 2015-07-08 2015-09-30 赤峰宝山能源（集团）贺麒铜业有限责任公司 一种直齿高低齿内螺纹传热管

Citations (4)

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JPH02165875A (ja) * 1988-12-16 1990-06-26 Furukawa Electric Co Ltd:The 伝熱管およびその製造方法
JPH0968396A (ja) * 1995-06-19 1997-03-11 Hitachi Ltd 熱交換器
JPH09318288A (ja) * 1996-05-30 1997-12-12 Sumitomo Light Metal Ind Ltd 内面溝付伝熱管
US5791405A (en) * 1995-07-14 1998-08-11 Mitsubishi Shindoh Co., Ltd. Heat transfer tube having grooved inner surface

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JPS5560089U (de) * 1978-10-12 1980-04-23
JPS6447880A (en) * 1987-08-18 1989-02-22 Nippon Steel Corp Stainless steel having ceramics layer on surface
JPH04288197A (ja) 1991-03-18 1992-10-13 Hitachi Ltd 洗濯機の洗濯制御方法
JP2721755B2 (ja) * 1991-05-16 1998-03-04 株式会社神戸製鋼所 伝熱管およびその製造方法
JP3286171B2 (ja) * 1996-08-06 2002-05-27 株式会社神戸製鋼所 内面溝付き伝熱管
JP3751393B2 (ja) * 1997-01-17 2006-03-01 株式会社コベルコ マテリアル銅管 管内面溝付伝熱管
JPH1183368A (ja) * 1997-09-17 1999-03-26 Hitachi Cable Ltd 内面溝付伝熱管
JPH1190530A (ja) * 1997-09-25 1999-04-06 Sumitomo Light Metal Ind Ltd 伝熱管の製造方法及び製造装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02165875A (ja) * 1988-12-16 1990-06-26 Furukawa Electric Co Ltd:The 伝熱管およびその製造方法
JPH0968396A (ja) * 1995-06-19 1997-03-11 Hitachi Ltd 熱交換器
US5791405A (en) * 1995-07-14 1998-08-11 Mitsubishi Shindoh Co., Ltd. Heat transfer tube having grooved inner surface
JPH09318288A (ja) * 1996-05-30 1997-12-12 Sumitomo Light Metal Ind Ltd 内面溝付伝熱管

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Title
PATENT ABSTRACTS OF JAPAN vol. 014, no. 420 (M-1023), 11 September 1990 (1990-09-11) -& JP 02 165875 A (FURUKAWA ELECTRIC CO LTD:THE), 26 June 1990 (1990-06-26) *
PATENT ABSTRACTS OF JAPAN vol. 1997, no. 07, 31 July 1997 (1997-07-31) -& JP 09 068396 A (HITACHI LTD), 11 March 1997 (1997-03-11) *
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 04, 31 March 1998 (1998-03-31) -& JP 09 318288 A (SUMITOMO LIGHT METAL IND LTD), 12 December 1997 (1997-12-12) *
See also references of WO0062001A1 *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1342971A2 (de) * 2002-03-07 2003-09-10 Wieland-Werke AG Wärmeaustauschrohr mit berippter Innenoberfläche
DE10210016A1 (de) * 2002-03-07 2003-09-25 Wieland Werke Ag Wärmeaustauschrohr mit berippter Innenoberfläche
EP1342971A3 (de) * 2002-03-07 2003-10-08 Wieland-Werke AG Wärmeaustauschrohr mit berippter Innenoberfläche
DE10210016B4 (de) * 2002-03-07 2004-01-08 Wieland-Werke Ag Wärmeaustauschrohr mit berippter Innenoberfläche
DE10210016B9 (de) * 2002-03-07 2004-09-09 Wieland-Werke Ag Wärmeaustauschrohr mit berippter Innenoberfläche
EP1852669A1 (de) * 2006-05-02 2007-11-07 Samsung Gwangju Electronics Co., Ltd. Wärmetauscher für einen Kühlschrank und Verfahren zur Herstellung eines Rohres dafür

Also Published As

Publication number Publication date
CN1313947A (zh) 2001-09-19
JP2000292088A (ja) 2000-10-20
AU746338B2 (en) 2002-04-18
AU3674800A (en) 2000-11-14
JP3296325B2 (ja) 2002-06-24
EP1087198A4 (de) 2005-04-27
WO2000062001A1 (fr) 2000-10-19

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