EP0518312A1 - Tube de transfert de chaleur à surface interne rayée - Google Patents

Tube de transfert de chaleur à surface interne rayée Download PDF

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Publication number
EP0518312A1
EP0518312A1 EP92109811A EP92109811A EP0518312A1 EP 0518312 A1 EP0518312 A1 EP 0518312A1 EP 92109811 A EP92109811 A EP 92109811A EP 92109811 A EP92109811 A EP 92109811A EP 0518312 A1 EP0518312 A1 EP 0518312A1
Authority
EP
European Patent Office
Prior art keywords
tube
heat transfer
grooves
transfer tube
grooved inner
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Withdrawn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
EP92109811A
Other languages
German (de)
English (en)
Inventor
Minoru Mizuno
Hiroshi Metoki
Hiroyuki Morita
Masahiko Kobayashi
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.)
Sumitomo Light Metal Industries Ltd
Original Assignee
Sumitomo Light Metal 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 Sumitomo Light Metal Industries Ltd filed Critical Sumitomo Light Metal Industries Ltd
Publication of EP0518312A1 publication Critical patent/EP0518312A1/fr
Withdrawn legal-status Critical Current

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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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
    • 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 used for the heat exchanger of air conditioners, refrigerators, and boilers; particularly to a heat transfer tube with grooved inner surface suitable for purposes in which a fluid flowing through the tube causes a phase change.
  • the heat transfer tube with grooved inner surface 1 has ridges (fins) 3 made by forming many spiral grooves 2 on the inner surface of a metallic tube such as a copper tube, which is used for purposes in which a fluid flowing through the tube causes a phase change between liquid and gas phases.
  • the factors determining the performance of the heat transfer tube with grooved inner surface under the above phase change state are considered to be the agitation effect by a fluid due to irregularity of the inner surface, heat transfer acceleration effect by increase of the inner surface area, and liquid-line fluctuation effect in the region of irregularity.
  • evaporation of a liquid is described below. The liquid flowing through a tube at a speed faster than a certain speed is quickly raised through an ultra-fine spiral groove by a combination of capillary action and the force caused by flow velocity to become a ring flow and evaporation is accelerated throughout the tube.
  • a heat transfer tube with grooved inner surface in actual use at present is disclosed in, for example, US Patent 4658892 and European Patent0148609.
  • Table 1 shows typical shape of the tube. Each dimensional item shown in Table 1 corresponds to that of Figs. 1 and 3.
  • Table 1 The heat transfer tube shown in Table 1 has a satisfactory heat transfer performance. However, it is desired to make the heat exchanger more compact, lightweight, and low cost, while improving the performance of the heat transfer tube and decrease its weight.
  • Table 1 Item Dimension Outside diameter of tube D mm 9.52 Inside diameter of tube Di mm 8.52 Groove depth (Fin height) Hf mm 0.20 Bottom wall thickness (Wall thickness from groove bottom to tube surface) Tf mm 0.30 Ridge apex angle (Fin apex angle) ⁇ Degree 53 Cross section perpendicular to grooves Lead angle (Helix angle of groove from tube axis) ⁇ Degree 18 Number of ridges (Number of fins) N - 60 Unit weight (Material: Copper) - g/m 94
  • the heat transfer tube with grooved inner surface for achieving these objects has been developed as the result of studying the correlation between the shape of grooves, shape of ridges (fins) formed between grooves, and heat transfer performance from various perspectives.
  • the heat transfer tube of the present invention premises that spiral grooves are formed on the inner surface, the helix angle of grooves from the tube axis (lead angle "alpha") ranges from 16 to 22°, the ratio (Hi/Di) of the groove depth (Hf) to the inside diameter of the tube (Di) ranges from 0.023 to 0.025, and the wall thickness between the groove bottom and the tube surface (bottom wall thickness Tf) ranges from 0.25 to 0.35 mm.
  • selection of the (Hf/Di) ratio is based mainly on the performance of the heat transfer tube, and the groove lead angle is determined by also considering the ease of manufacturing the heat transfer tube.
  • the heat transfer tube of the present invention obtains maximum heat transfer performance by combining these prerequisites with requirements for the shape of grooves and ridges to be described later. It is preferable for the outside diameter of the tube (D) to range between 9.5 and 10 mm.
  • the first requirement for shape in the present invention is to keep the ratio (W/Hf) of the groove bottom width (W) to the groove depth or fin height (Hf) on a cross section perpendicular to the axis at a range of 1.22 to 1.27.
  • a ratio (W/Hf) of less than 1.22 if the condensate of a fluid in the tube remains in the grooves, the fins will easily become covered and condensation capacity will decrease.
  • the inner surface area of the tube decreases and the heat transfer performance drops.
  • the ratio (W/Hf) exceeds the specified range of the present invention.
  • the second requirement for shape in the present invention is to set the apex angle (gamma) of the ridge (fin) to 50-55° on a cross section perpendicular to grooves.
  • the apex angle (gamma) decreases, the heat transfer performance is improved both for evaporation and condensation.
  • the present invention makes it possible to obtain a lightweight heat transfer tube with grooved inner surface with a satisfactory machinability for manufacturing tubes by keeping the ratio (W/Hf) of the groove bottom width (W) to the fin height (Hf) within the above mentioned range to specify the groove shape, combining the specified groove shape with the fin shape whose apex angle is limited to accelerate heat transfer, and properly keeping the flow line of their regular region to improve performance.
  • Evaporation and condensation tests are performed by using Freon-R22 as a refrigerant and pouring the refrigerant into the heat transfer tube of the present invention with spiral grooves on its inner surface and having the dimensions in Table 3 by changing the refrigerant flow rate in accordance with the conditions shown in Table 2.
  • Fig. 4 shows the relationship between the refrigerant flow rate and the vaporization heat transfer rate on the heat transfer tube obtained through the above tests and Fig. 5 shows the relationship between the refrigerant flow rate and the condensation heat transfer rate on it.
  • a condensation test is applied to the heat transfer tube of the present invention with spiral grooves on its inner surface and having the dimensions shown in Table 3 by changing the fin width (groove width) of the tube to change the ratio (W/Hf) of the groove width (W) to Hf on a cross section perpendicular to the axis under the same conditions as in embodiment 1.
  • the refrigerant flow rate is set to 50 kg/h.
  • Fig. 6 shows the test results.
  • the present invention makes it possible to provide a heat transfer tube with grooved inner surface superior in heat transfer performance and more lightweight than the conventional tube while decreasing the cost of heat exchangers.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Metal Extraction Processes (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)
EP92109811A 1991-06-11 1992-06-11 Tube de transfert de chaleur à surface interne rayée Withdrawn EP0518312A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP16762591A JPH0579783A (ja) 1991-06-11 1991-06-11 内面溝付伝熱管
JP167625/91 1991-06-11

Publications (1)

Publication Number Publication Date
EP0518312A1 true EP0518312A1 (fr) 1992-12-16

Family

ID=15853262

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92109811A Withdrawn EP0518312A1 (fr) 1991-06-11 1992-06-11 Tube de transfert de chaleur à surface interne rayée

Country Status (3)

Country Link
EP (1) EP0518312A1 (fr)
JP (1) JPH0579783A (fr)
FI (1) FI922701A (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0603108A1 (fr) * 1992-12-16 1994-06-22 Carrier Corporation Tube d'échangeur de chaleur
FR2706197A1 (fr) * 1993-06-07 1994-12-16 Trefimetaux Tubes rainurés pour échangeurs thermiques d'appareils de conditionnement d'air et de réfrigération, et échangeurs correspondants.
US6164370A (en) * 1993-07-16 2000-12-26 Olin Corporation Enhanced heat exchange tube
US6173763B1 (en) * 1994-10-28 2001-01-16 Kabushiki Kaisha Toshiba Heat exchanger tube and method for manufacturing a heat exchanger
WO2001063196A1 (fr) * 2000-02-25 2001-08-30 The Furukawa Electric Co., Ltd. Tube comportant des rainures sur sa surface interieure et procede de fabrication associe
WO2003076861A1 (fr) * 2002-03-12 2003-09-18 Trefimetaux Tubes rainures a utilisation reversible pour echangeurs thermiques

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007271220A (ja) * 2006-03-31 2007-10-18 Kobelco & Materials Copper Tube Inc ガスクーラー用内面溝付伝熱管

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2552679A1 (de) * 1974-11-25 1976-06-16 Hitachi Ltd Waermeuebertragungsrohr
EP0148609A2 (fr) * 1983-12-28 1985-07-17 Hitachi Cable, Ltd. Tubes de transfert de chaleur à surface interne rayée
DE3414230A1 (de) * 1984-04-14 1985-10-24 Ernst Behm Waermetauscherrohr

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2552679A1 (de) * 1974-11-25 1976-06-16 Hitachi Ltd Waermeuebertragungsrohr
EP0148609A2 (fr) * 1983-12-28 1985-07-17 Hitachi Cable, Ltd. Tubes de transfert de chaleur à surface interne rayée
US4658892A (en) * 1983-12-28 1987-04-21 Hitachi Cable, Ltd. Heat-transfer tubes with grooved inner surface
US4658892B1 (fr) * 1983-12-28 1990-04-17 Hitachi Cable
DE3414230A1 (de) * 1984-04-14 1985-10-24 Ernst Behm Waermetauscherrohr

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0603108A1 (fr) * 1992-12-16 1994-06-22 Carrier Corporation Tube d'échangeur de chaleur
FR2706197A1 (fr) * 1993-06-07 1994-12-16 Trefimetaux Tubes rainurés pour échangeurs thermiques d'appareils de conditionnement d'air et de réfrigération, et échangeurs correspondants.
WO1994029661A1 (fr) * 1993-06-07 1994-12-22 Trefimetaux Tubes rainures pour echangeurs thermiques d'appareils de conditionnement d'air et de refrigeration, et echangeurs correspondants
AU677850B2 (en) * 1993-06-07 1997-05-08 Trefimetaux Grooved tubes for heat exchangers used in air conditioning and cooling apparatuses, and corresponding exchangers
US6164370A (en) * 1993-07-16 2000-12-26 Olin Corporation Enhanced heat exchange tube
US6173763B1 (en) * 1994-10-28 2001-01-16 Kabushiki Kaisha Toshiba Heat exchanger tube and method for manufacturing a heat exchanger
WO2001063196A1 (fr) * 2000-02-25 2001-08-30 The Furukawa Electric Co., Ltd. Tube comportant des rainures sur sa surface interieure et procede de fabrication associe
WO2003076861A1 (fr) * 2002-03-12 2003-09-18 Trefimetaux Tubes rainures a utilisation reversible pour echangeurs thermiques
FR2837270A1 (fr) * 2002-03-12 2003-09-19 Trefimetaux Tubes rainures a utilisation reversible pour echangeurs thermiques
US7048043B2 (en) 2002-03-12 2006-05-23 Trefimetaux Reversible grooved tubes for heat exchangers
NO338468B1 (no) * 2002-03-12 2016-08-22 Trefimetaux Rør med spor for reversibel bruk med varmevekslere
HRP20040819B1 (hr) * 2002-03-12 2017-12-01 Trefimetaux S.A. Cijevi s utorima za reverzibilno korištenje kod izmjenjivača topline

Also Published As

Publication number Publication date
JPH0579783A (ja) 1993-03-30
FI922701A (fi) 1992-12-12
FI922701A0 (fi) 1992-06-10

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