EP2354743A2 - Échangeur thermique à double tuyau - Google Patents

Échangeur thermique à double tuyau Download PDF

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Publication number
EP2354743A2
EP2354743A2 EP11150467A EP11150467A EP2354743A2 EP 2354743 A2 EP2354743 A2 EP 2354743A2 EP 11150467 A EP11150467 A EP 11150467A EP 11150467 A EP11150467 A EP 11150467A EP 2354743 A2 EP2354743 A2 EP 2354743A2
Authority
EP
European Patent Office
Prior art keywords
heat exchange
exchange tube
fluid
double
heat exchanger
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Withdrawn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
EP11150467A
Other languages
German (de)
English (en)
Other versions
EP2354743A3 (fr
Inventor
Hongseong Kim
Sangyeul Lee
Yongcheol Sa
Hanchoon Lee
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.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
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 LG Electronics Inc filed Critical LG Electronics Inc
Publication of EP2354743A2 publication Critical patent/EP2354743A2/fr
Publication of EP2354743A3 publication Critical patent/EP2354743A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/06—Heat exchange conduits having walls comprising obliquely extending corrugations, e.g. in the form of threads

Definitions

  • a double-pipe heat exchanger is disclosed herein.
  • Heat exchangers are known. However, they suffer from various disadvantages.
  • Fig. 1 is a cross-sectional view of a double-pipe heat exchanger according to an embodiment
  • Fig. 2 is an enlarged view of portion A of Fig. 1 ;
  • Fig. 3 is a graph showing a relationship between heat transfer performance and a pitch W of a spiral part in a double-pipe heat exchanger according to an embodiment.
  • a heat exchanger is a device that transfers thermal energy from a high temperature fluid to a relatively low temperature fluid, thereby cooling the high temperature fluid and heating the low temperature fluid.
  • the heat exchanger may be used in, for example, a heater, a cooler, an evaporator, or a condenser.
  • a heat transfer medium used in the heat exchanger may be classified as a heating medium that transfers heat to a subject or target fluid, and a cooling medium that absorbs heat from the subject or target fluid.
  • the cooling or heating medium may be used in the gaseous or liquid state.
  • a double-pipe heat exchanger may include an internal tube into which a first fluid is introduced and flows, and an external tube disposed so as to enclose the internal tube and into which a second fluid is introduced and flows.
  • a side wall of the internal tube may be used as a heat transfer wall that performs heat exchange between the first and second fluids.
  • a heat transfer surface area between the second fluid and an outer wall of the internal tube may be small, and thus, heat exchange efficiency very low.
  • a scale of the heat exchanger or a length of the double pipe may be increased.
  • Fig. 1 is a cross-sectional view of a double-pipe heat exchanger according to an embodiment
  • Fig. 2 is an enlarged view of portion A of Fig. 1
  • a double-pipe heat exchanger 300 may include a first heat exchange tube 100 and a second heat exchange tube 200.
  • the first heat exchange tube 100 may be formed in a pipe shape having a first hollow portion 110.
  • the first heat exchange tube 100 may have a first diameter D1.
  • the first heat exchange tube 100 may include a first fluid inlet port 120 that communicates with the first heat exchange tube 100 and a first fluid outlet port 130 that communicates with the first heat exchange tube 100.
  • a first fluid may be introduced into and flow through the first fluid inlet port 120, and may be discharged through the first fluid outlet port 130 after heat exchange.
  • the first fluid which is introduced through the first fluid inlet port 120 and is then discharged through the first fluid outlet port 130 may be a single-phase fluid, for example, cooling water. Further, the first fluid may have a first temperature.
  • the second heat exchange tube 200 may be disposed inside the first heat exchange tube 100, so that the first and second heat exchange tubes 100 and 200 are coaxial.
  • the second heat exchange tube 200 may have a second diameter D2 smaller than the first diameter D1 of the first heat exchange tube 100, and thus, a gap G may be formed between the first and second heat exchange tubes 100 and 200.
  • the first fluid may pass through the gap G between the first and second heat exchange tubes 100 and 200.
  • the second diameter D2 of the second heat exchange tube 200 may be about 19.05 mm.
  • the second heat exchange tube 200 disposed inside the first heat exchange tube 100 may have a spiral part 210.
  • the spiral part 210 may be formed at a surface of the second heat exchange tube 200 so as to be in the form of a screw, and the screw-shaped spiral part 210 may have multiple ridges 212 and grooves 214.
  • the spiral part 210 may be formed at both inner and outer surfaces of the second heat exchange tube 200.
  • the ridges 212 and grooves 214 of the spiral part 210 may be formed by, for example, a processing roller.
  • a second fluid inlet port 202 which may be cylindrical, may be formed at one end of the second heat exchange tube 200, and a second fluid outlet port 204, which may be cylindrical, may be formed at the other end thereof.
  • a second fluid may be introduced into and flow through the second fluid inlet port 202 and may be discharged through the second fluid outlet port 204 after heat exchange.
  • the second fluid provided in the second heat exchange tube 200 may be a two-phase fluid.
  • the second fluid may be converted from a liquid state to a gaseous state within the second heat exchange tube 200.
  • the second fluid provided in the second heat exchange tube 200 may be a single-phase fluid.
  • the second fluid may have a second temperature that is different from the first temperature of the first fluid.
  • the first temperature of the first fluid may be higher than the second temperature of the second fluid.
  • the first temperature of the first fluid may be lower than the second temperature of the second fluid.
  • a pitch W of the spiral part 210 of the second heat exchange tube 200 and a height difference Hc between the ridges 212 and grooves 214 formed by the spiral part 210 have a great influence on the heat transfer performance of the first and second heat exchange tubes 100 and 200. If the height difference Hc and the pitch W of the spiral part 210 are not optimized, the heat transfer performance may be reduced or deteriorated.
  • Fig. 3 is a graph showing a relationship between heat transfer performance and a pitch W of a spiral part in a double-pipe heat exchanger according to an embodiment.
  • the X axis of the graph in Fig. 3 designates the pitch W of the spiral part 210 and the Y axis designates the heat transfer performance.
  • the heat transfer performance of the double-pipe heat exchanger 300 in Fig. 1 decreases.
  • the pitch W of the spiral part 210 is about 4 ⁇ 10 mm, a heat transfer characteristic of the double-pipe heat exchanger 300 is within an allowable range.
  • the pitch W of the spiral part 210 of the second heat exchange tube 200 is less than about 4 mm, the heat transfer characteristic increases, but it is difficult to manufacture and process the pitch W of the spiral part 210.
  • the pitch W of the spiral part 210 of the second heat exchange tube 200 is larger than about 10 mm, the heat transfer characteristic decreases. Therefore, the pitch W of the spiral part 210 may be about 4 ⁇ 10 mm in consideration of working and heat transfer characteristics.
  • the height difference Hc between the ridges 212 and grooves 214 of the spiral part 210 of the second heat transfer pipe 200 may be about 1 ⁇ 3 mm.
  • the height difference Hc between the ridges 212 and grooves 214 is less than about 1 mm, heat transfer efficiency decreases remarkably.
  • the height difference Hc between the ridges 212 and grooves 214 is larger than about 3 mm, the heat transfer efficiency increases, but it is difficult to manufacture and process the pitch W of the spiral part 210. Therefore, the height difference Hc between the ridges 212 and grooves 214 of the spiral part 210 may be about 1 ⁇ 3 mm in order to satisfy working and heat transfer characteristics.
  • a ratio A/W which is a distance A between a half point W/2 of the pitch W and a top portion P of the ridge 212 divided by the pitch W may be less than about 0.15.
  • the second fluid which is converted from liquid phase to gaseous phase, is provided in the second heat exchange tube 200, the second fluid may be rotated at a high speed by the spiral part 210 of the second heat transfer tube 200.
  • the liquid-phase second fluid having a higher density than the gaseous-phase second fluid may be mainly distributed at an inner side surface of the spiral part 210, and the gaseous-phase second fluid having a relatively low density may be mostly distributed at a center portion of the spiral part 210.
  • liquid-phase second fluid and the gaseous-phase second fluid may be separated from each other by a cyclone effect.
  • the liquid-phase second fluid distributed at the inner side surface of the spiral part 210 may be actively heat-exchanged with the first fluid provided in the first heat exchange tube 100, and thus, the heat exchange characteristics between the first and second fluids may be further improved.
  • the spiral part may be formed on a surface of the second heat exchange tube disposed inside the first heat exchange tube, and the pitch and height of the spiral portion may be optimized, improving considerably the heat transfer efficiency.
  • Embodiments disclosed herein provide a double-pipe heat exchanger in which a heat exchange tube disposed at a relatively inner side may be formed in a spiral shape in which ridges and grooves may be continuously formed, thereby increasing a heat transfer performance.
  • a double-pipe heat exchanger may include a first heat exchange tube having a first hollow portion, and a second heat exchange tube disposed inside the first heat exchange tube so as to be co-axial with the first heat exchange tube and having a spiral part in which multiple ridges and grooves may be formed at an inner surface of the spiral part.
  • the second heat exchange tube may include a cylindrical second fluid inlet port, which may be inserted into or provided at one side of the first heat exchange tube and through which a second fluid may pass; a cylindrical second fluid outlet port, which may be inserted into or provided at the other side of the first heat exchange tube and through which the second fluid may be discharged; and a screw-shaped spiral part continuously formed between the second fluid inlet port and the second fluid outlet port.
  • a ratio A/W of a pitch W that is a length between adjacent grooves of the second heat exchange tube to a distance A between a center portion of the pitch W and a top portion P of the ridge may be less than about approximately 0.15.
  • the pitch W may be approximately 4 mm ⁇ W ⁇ 10 mm, and a height difference Hc between the adjacent ridges and grooves may be approximately 1 mm ⁇ Hc ⁇ 3 mm.
  • a temperature of a first fluid provided between the first and second heat exchange tubes may be different from that of a second fluid provided in the second heat exchange tube.
  • the second fluid provided in the second heat exchange tube may be one of a single-phase fluid or a two-phase fluid.
  • any reference in this specification to "one embodiment,” “an embodiment,” “example embodiment,” etc. means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the invention.
  • the appearances of such phrases in various places in the specification are not necessarily all referring to the same embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP11150467A 2010-01-15 2011-01-10 Échangeur thermique à double tuyau Withdrawn EP2354743A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020100004010A KR101620106B1 (ko) 2010-01-15 2010-01-15 이중 열교환기

Publications (2)

Publication Number Publication Date
EP2354743A2 true EP2354743A2 (fr) 2011-08-10
EP2354743A3 EP2354743A3 (fr) 2012-10-31

Family

ID=43859119

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11150467A Withdrawn EP2354743A3 (fr) 2010-01-15 2011-01-10 Échangeur thermique à double tuyau

Country Status (4)

Country Link
US (1) US20110174469A1 (fr)
EP (1) EP2354743A3 (fr)
KR (1) KR101620106B1 (fr)
CN (1) CN102128554A (fr)

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CN102368024A (zh) * 2011-09-19 2012-03-07 福兴织造（苏州）有限公司 纺织厂余热回收装置
KR101354814B1 (ko) * 2011-12-14 2014-01-27 삼성전기주식회사 반도체 패키지
US20150159964A1 (en) * 2012-05-07 2015-06-11 Tetra Laval Holdings & Finance S.A. Tubular heat exchanger
US10132538B2 (en) * 2012-05-25 2018-11-20 Hussmann Corporation Heat exchanger with integrated subcooler
CN102831941B (zh) * 2012-06-11 2015-04-15 华北电力大学 一种0型铅铋换热装置
FR3016689B1 (fr) * 2014-01-20 2016-01-15 Vallourec Heat Exchanger Tubes Tube ameliore pour echangeur thermique
JP6223298B2 (ja) * 2014-07-31 2017-11-01 株式会社コベルコ マテリアル銅管 管内単相流用伝熱管
CN104578977A (zh) * 2015-01-05 2015-04-29 武汉理工大学 一种汽车尾气热电发电装置
CN105202794B (zh) * 2015-09-29 2018-01-19 美的集团武汉制冷设备有限公司 空调器
CN105515447B (zh) * 2016-01-05 2017-12-29 武汉理工大学 一种汽车尾气温差发电热交换装置
CN106403659A (zh) * 2016-11-17 2017-02-15 北京蓝爱迪电力技术有限公司 一种套管式气固高速两相流高效加热设备
CN107238308A (zh) * 2017-07-25 2017-10-10 陕西路圣里德太阳能研究院有限公司 导热油‑水翅片管换热管组及储能装置
GB2569306A (en) * 2017-12-12 2019-06-19 Rolls Royce Plc Thermal management device
CN108225057A (zh) * 2018-02-11 2018-06-29 佛山科学技术学院 一种凹面换热管套管式换热器
US11221182B2 (en) * 2018-07-31 2022-01-11 Applied Materials, Inc. Apparatus with multistaged cooling
CN109578806B (zh) * 2018-12-07 2024-01-23 江苏中圣压力容器装备制造有限公司 一种lng闪蒸汽（bog）增压冷凝回收的工艺装置
CN112413916B (zh) * 2020-11-16 2022-01-07 中科赛凌（北京）科技有限公司 一种冷热气喷射装置
CN113432458B (zh) * 2021-07-12 2022-04-01 湖北中油科昊机械制造有限公司 一种用于压裂车冷却装置
CN115127371B (zh) * 2021-12-14 2024-09-13 中国石油天然气集团有限公司 管内旋流式耐粘附性介质蒸发器

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Also Published As

Publication number Publication date
CN102128554A (zh) 2011-07-20
EP2354743A3 (fr) 2012-10-31
KR20110083996A (ko) 2011-07-21
US20110174469A1 (en) 2011-07-21
KR101620106B1 (ko) 2016-05-13

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