US20130306288A1 - Tube structures for heat exchanger - Google Patents

Tube structures for heat exchanger Download PDF

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Publication number
US20130306288A1
US20130306288A1 US13/981,364 US201213981364A US2013306288A1 US 20130306288 A1 US20130306288 A1 US 20130306288A1 US 201213981364 A US201213981364 A US 201213981364A US 2013306288 A1 US2013306288 A1 US 2013306288A1
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US
United States
Prior art keywords
tube
ridges
ratio
heat exchanger
ridge
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.)
Abandoned
Application number
US13/981,364
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English (en)
Inventor
Michael F. Taras
Sunil S. Mehendale
Mel Woldesemayat
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Carrier Corp
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Carrier Corp
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Publication date
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Priority to US13/981,364 priority Critical patent/US20130306288A1/en
Assigned to CARRIER CORPORATION reassignment CARRIER CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WOLDESEMAYAT, Mel, MEHENDALE, SUNIL S., TARAS, MICHAEL F.
Assigned to CARRIER CORPORATION reassignment CARRIER CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WOLDESEMAYAT, Mel, MEHENDALE, SUNIL S., TARAS, MICHAEL F.
Publication of US20130306288A1 publication Critical patent/US20130306288A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • 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
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal

Definitions

  • the subject matter disclosed herein relates to heat exchangers. More specifically, the subject disclosure relates to improved tube structures for a heat exchanger.
  • a simplified typical vapor compression refrigeration cycle includes an evaporator, a compressor, a condenser and an expansion device.
  • Refrigerant flow is such that low pressure refrigerant vapor passes through a suction line to the compressor.
  • the compressed refrigerant vapor is pumped to a discharge line that connects to the condenser.
  • a liquid line receives liquid refrigerant exiting the condenser and directs it to the expansion device.
  • a two-phase refrigerant is returned to the evaporator, thereby completing the cycle.
  • evaporator and condenser heat exchangers Two of the main components in a vapor compression cycle are the evaporator and condenser heat exchangers.
  • the most common type of heat exchanger in use is of the round tube plate fin (RTPF) construction type.
  • RTPF round tube plate fin
  • the tubes were made of copper while the fins were typically made of aluminum in such heat exchangers.
  • the thermal performance of a heat exchanger is inversely proportional to the sum of its thermal resistances.
  • HVAC&R heating, ventilation, air conditioning and refrigeration
  • the airside thermal resistance contributes 50-70% while refrigerant side thermal resistance is 20-40% and the metal resistance is relatively small and represents only 6-10%. Due to the continuous market pressure and regulatory requirements to make HVAC&R units more compact and cost effective, a lot of effort has been devoted to improving the heat exchanger performance on the refrigerant side as well as the airside.
  • a fluid-carrying tube for a heat exchanger includes an outer perimeter, an inner perimeter, and a plurality of ridges extending from the inner perimeter inwardly into an interior of the tube.
  • Each ridge includes a ridge height, a base width and a tip width.
  • a ratio of the ridge height to the base width is between about 0.2 and about 4.0, and a ratio of the tip width to the base width is between about 0.015 and about 0.965.
  • a heat exchanger includes a plurality of fins and a plurality of tubes passing a fluid therethrough and extending through the plurality of fins.
  • At least one tube of the plurality of tubes includes an outer perimeter, an inner perimeter, and a plurality of ridges extending from the inner perimeter inwardly into an interior of the at least one tube.
  • Each ridge has a ridge height, a base width, and a tip width.
  • a ratio of the ridge height to the base width is between about 0.2 and about 4.0, and a ratio of the tip width to the base width is between about 0.015 and about 0.965.
  • FIG. 1 is a schematic view of an embodiment of a heat exchanger
  • FIG. 2 is a partial cross-sectional view of an embodiment of a heat exchanger tube
  • FIG. 3 is a cross-sectional view of an embodiment of a heat exchanger tube.
  • FIG. 1 Shown in FIG. 1 is an embodiment of a round tube plate fin (RTPF) heat exchanger 10 , such as one utilized as an evaporator or condenser.
  • the RTPF heat exchanger 10 includes a plurality of tubes 12 and a plurality of fins 14 .
  • the plurality of tubes 12 carry a fluid, for example, a refrigerant. Thermal energy is exchanged between the fluid and air flowing past the plurality of fins 14 .
  • the tubes 12 may be formed of an aluminum or aluminum alloy by, for example, an extrusion process, while in other embodiments, the tubes 12 maybe formed of other materials, for example, copper, Cu—Ni, steel or plastic.
  • FIG. 2 illustrates a partial cross-sectional view of a tube 12 of a heat exchanger 10 .
  • the tube 12 includes a plurality of enhancements, or ridges 16 extending into an interior 18 of the tube 12 .
  • the tube 12 has an outer perimeter 32 and an inner perimeter 34 , with the ridges 16 extending inwardly from the inner perimeter 34 into the interior 18 of the tube 12 .
  • the ridges 16 extend along a length 20 of the tube 12 .
  • the ridges 16 extend substantially axially, while in other embodiments, the ridges 16 extend helically along the tube 12 at a helix angle ⁇ with respect to a tube axis 24 .
  • Ridges 16 improve the heat transfer characteristics of the tubes 12 while maintaining a balance with pressure drop requirements to achieve a desired refrigerant flow through the tubes 12 .
  • Specific geometric configurations of the ridges 16 enhancing both the pre-expansion and post-expansion tube 12 surface geometry, are described below by way of example.
  • the ridges 16 have a number of characteristics to define their shape and arrangement in the interior 18 of the tube 12 .
  • Each ridge 16 has a ridge 16 height h, a base 26 width w, and a tip 28 width b. Sides 30 of the ridge 16 extend from the base 26 to the tip 28 at an apex angle Y. Adjacent ridges 16 are spaced by a ridge 16 pitch P r .
  • Each tube 12 has a tube diameter D, and a baseline tube 12 wall thickness t b between adjacent ridges 16 .
  • Shape of the ridges 16 , as well as ridge 16 pitch P r and a number of ridges 16 in the tube 12 , N r , are all taken into account when comparing an internal surface area of a tube 12 including the ridges 16 to a typical tube having a smooth wall, and thus an internal diameter as shown in equation (1) of:
  • the increased internal surface area of the tube 12 including ridges 16 compared to the smooth-walled tube increases the effectiveness of thermal energy transfer between fluid in the tube 12 and an external environment.
  • the effect of the increased surface area can be expressed as an enhancement ratio R x as in equation (2) below:
  • R x (2* h*N r *((1-sin(Y/2)/( ⁇ *( D ⁇ 2 *( t b +h ))*cos( Y/ 2)))+1)/cos ⁇ (2)
  • the enhancement ratio Rx is a strong linear function of h/( ⁇ *(D ⁇ 2 *(t b +h))/N r ), which is a ratio of the ridge height h, to the ridge pitch P r .
  • the ridges 16 may extend substantially axially along the length 20 , or may extend at helix angle a of between about 18 degrees and about 35 degrees. Further, a ratio of the number of ridges Nr to a maximum internal diameter of the tube 12 , or N r /D imax may be between about 5.4 and about 10.1, where D imax is specified in millimeters. In some embodiments, a ratio of the ridge height, h, to the ridge pitch, P r , is between about 0.17 and about 1.36. R x , as shown in equation 1, is between about 1.28 and about 3.49 in some embodiments, for example, those where the ridges 16 extend substantially axially along the tube 12 .
  • R x is between about 1.34 and about 4.26.
  • a ratio ridge height h to maximum internal diameter of the tube 12 , or MD. is between about 0.0008 and about 0.0870.
  • the apex angle Y is between about 10 degrees and 25 degrees.
  • the ridge height h and base width w are related such that a ratio of the ridge height to the base width, or h/w is between about 0.2 and about 4.0.
  • the tip width b and the base width w, or b/w is between about 0.015 and about 0.965.
  • N r /D imax may be between about 5.4 and about 9.25.
  • h/P r is between about 0.17 and about 1.22.
  • R x is between about 1.28 and about 3.23 in embodiments where the ridges 16 extend substantially axially along the tube 12 and where the helix angle ⁇ is not zero, R x is between about 1.34 and about 3.94.
  • h/D imax is between about 0.0008 and about 0.035.
  • N r /D imax where D imax is expressed in millimeters, may be between about 5.8 and about 10.1.
  • h/P r is between about 0.19 and about 1.36.
  • R x is between about 1.30 and about 3.49 in embodiments where the ridges 16 extend substantially axially along the tube 12 and where the helix angle ⁇ is not zero, R x is between about 1.37 and about 4.26.
  • h/D imax is between about 0.0117 and about 0.0488.
  • N r /D imax may be between about 5.4 and about 9.5, where D imax is specified in millimeters.
  • h/P r is between about 0.18 and about 1.30.
  • R x is between about 1.28 and about 3.37 in embodiments where the ridges 16 extend substantially axially along the tube 12 and where the helix angle ⁇ is not zero, R x is between about 1.35 and about 4.12.
  • h/D imax is between about 0.021 and about 0.087.
  • N r /D imax may be between about 5.5 and about 9.4, where D imax is specified in millimeters.
  • h/P r is between about 0.18 and about 1.30.
  • R x is between about 1.29 and about 3.39 in embodiments where the ridges 16 extend substantially axially along the tube 12 and where the helix angle a is not zero, R x is between about 1.36 and about 4.14.
  • h/D imax is between about 0.021 and about 0.087.
  • tubes 12 illustrated herein are substantially circular, it is to be appreciated that, in other embodiments, the tubes 12 may be noncircular in cross-section having, for example, an oval, an elliptical, or a race-track cross-section.
  • an equivalent to tube 12 diameter D would be a circular cross-section tube diameter that would have identical mass or material content in the cross-section as the particular non-circular cross-section. All geometrical ratios described hereabove are equally applicable to such non-circular tube configurations allowing achieving substantially improved in-tube thermal and hydraulic performance.
  • tubes 12 including such ridges 16 that conform to the exemplary ranges of these ratios exhibit substantially improved thermo-hydraulic performance over prior art tubes.
  • the ratios, and described ranges for the ratios, are not obvious and have been developed via extensive simulation and experimentation on the component and sub-component level, while specifically focusing on the two-phase refrigerant flows.

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  • 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)
US13/981,364 2011-01-28 2012-01-26 Tube structures for heat exchanger Abandoned US20130306288A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US13/981,364 US20130306288A1 (en) 2011-01-28 2012-01-26 Tube structures for heat exchanger

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US201161437427P 2011-01-28 2011-01-28
US13/981,364 US20130306288A1 (en) 2011-01-28 2012-01-26 Tube structures for heat exchanger
PCT/US2012/022641 WO2012103278A1 (en) 2011-01-28 2012-01-26 Tube structures for heat exchanger

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US20130306288A1 true US20130306288A1 (en) 2013-11-21

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Country Status (4)

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US (1) US20130306288A1 (de)
EP (1) EP2668460A1 (de)
CN (1) CN103339460B (de)
WO (1) WO2012103278A1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180038654A1 (en) * 2016-08-08 2018-02-08 General Electric Company System for fault tolerant passage arrangements for heat exchanger applications
US11662150B2 (en) 2020-08-13 2023-05-30 General Electric Company Heat exchanger having curved fluid passages for a gas turbine engine
US12006870B2 (en) 2020-12-10 2024-06-11 General Electric Company Heat exchanger for an aircraft

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112577355A (zh) * 2019-09-27 2021-03-30 约克（无锡）空调冷冻设备有限公司 一种换热管、换热器及使用该换热器的空调系统

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1895287A (en) * 1931-10-15 1933-01-24 Heintz Mfg Co Fin radlator
US3831675A (en) * 1972-01-17 1974-08-27 Olin Corp Heat exchanger tube
US5259448A (en) * 1991-07-09 1993-11-09 Mitsubishi Shindoh Co., Ltd. Heat transfer tubes and method for manufacturing
US5862857A (en) * 1995-07-12 1999-01-26 Sanyo Electric Co., Ltd Heat exchanger for refrigerating cycle
US6164370A (en) * 1993-07-16 2000-12-26 Olin Corporation Enhanced heat exchange tube
US20030006031A1 (en) * 2000-08-25 2003-01-09 Wieland-Werke Ag Internally finned heat transfer tube with staggered fins of varying height
US20070089868A1 (en) * 2005-10-25 2007-04-26 Hitachi Cable, Ltd. Heat transfer pipe with grooved inner surface

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JP2001343194A (ja) * 2000-05-31 2001-12-14 Mitsubishi Shindoh Co Ltd 内面溝付伝熱管および熱交換装置
JP2003222487A (ja) * 2002-01-31 2003-08-08 Kobe Steel Ltd プレートフィンチューブ型熱交換器用内面溝付管及びプレートフィンチューブ型熱交換器
FR2837270B1 (fr) * 2002-03-12 2004-10-01 Trefimetaux Tubes rainures a utilisation reversible pour echangeurs thermiques
JP3964244B2 (ja) * 2002-03-27 2007-08-22 株式会社コベルコ マテリアル銅管 内面溝付管
JP4422590B2 (ja) * 2004-09-02 2010-02-24 株式会社コベルコ マテリアル銅管 リターンベンド管およびフィンアンドチューブ型熱交換器
JP2007271123A (ja) * 2006-03-30 2007-10-18 Kobelco & Materials Copper Tube Inc 内面溝付伝熱管
CN201081590Y (zh) * 2007-07-26 2008-07-02 上海龙阳精密复合铜管有限公司 瘦高型齿内螺纹无缝高效传热管
KR20090022841A (ko) * 2007-08-31 2009-03-04 엘지전자 주식회사 냉동 장치의 열교환기 및 그 냉매 튜브와 그 제조 방법
DE102008024562B4 (de) * 2008-05-21 2021-06-10 Stiebel Eltron Gmbh & Co. Kg Wärmepumpenvorrichtung mit einem Lamellenrohrwärmeübertrager als Verdampfer

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1895287A (en) * 1931-10-15 1933-01-24 Heintz Mfg Co Fin radlator
US3831675A (en) * 1972-01-17 1974-08-27 Olin Corp Heat exchanger tube
US5259448A (en) * 1991-07-09 1993-11-09 Mitsubishi Shindoh Co., Ltd. Heat transfer tubes and method for manufacturing
US6164370A (en) * 1993-07-16 2000-12-26 Olin Corporation Enhanced heat exchange tube
US5862857A (en) * 1995-07-12 1999-01-26 Sanyo Electric Co., Ltd Heat exchanger for refrigerating cycle
US20030006031A1 (en) * 2000-08-25 2003-01-09 Wieland-Werke Ag Internally finned heat transfer tube with staggered fins of varying height
US20070089868A1 (en) * 2005-10-25 2007-04-26 Hitachi Cable, Ltd. Heat transfer pipe with grooved inner surface

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180038654A1 (en) * 2016-08-08 2018-02-08 General Electric Company System for fault tolerant passage arrangements for heat exchanger applications
US11662150B2 (en) 2020-08-13 2023-05-30 General Electric Company Heat exchanger having curved fluid passages for a gas turbine engine
US12006870B2 (en) 2020-12-10 2024-06-11 General Electric Company Heat exchanger for an aircraft

Also Published As

Publication number Publication date
CN103339460B (zh) 2017-01-18
WO2012103278A1 (en) 2012-08-02
CN103339460A (zh) 2013-10-02
EP2668460A1 (de) 2013-12-04

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Owner name: CARRIER CORPORATION, CONNECTICUT

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TARAS, MICHAEL F.;MEHENDALE, SUNIL S.;WOLDESEMAYAT, MEL;SIGNING DATES FROM 20110128 TO 20110131;REEL/FRAME:028208/0883

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Owner name: CARRIER CORPORATION, CONNECTICUT

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TARAS, MICHAEL F.;MEHENDALE, SUNIL S.;WOLDESEMAYAT, MEL;SIGNING DATES FROM 20110128 TO 20110131;REEL/FRAME:030864/0125

STCB Information on status: application discontinuation

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