EP1851498B1 - Tubes rainures a utilisation reversible pour echangeurs thermiques - Google Patents

Tubes rainures a utilisation reversible pour echangeurs thermiques Download PDF

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Publication number
EP1851498B1
EP1851498B1 EP03743918.9A EP03743918A EP1851498B1 EP 1851498 B1 EP1851498 B1 EP 1851498B1 EP 03743918 A EP03743918 A EP 03743918A EP 1851498 B1 EP1851498 B1 EP 1851498B1
Authority
EP
European Patent Office
Prior art keywords
tubes
use according
ribs
ranging
tube
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.)
Expired - Lifetime
Application number
EP03743918.9A
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German (de)
English (en)
French (fr)
Other versions
EP1851498A1 (fr
Inventor
Pascal Leterrible
Nicolas Avanan
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.)
KME FRANCE Sas
Original Assignee
KME France Sas
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Filing date
Publication date
Application filed by KME France Sas filed Critical KME France Sas
Publication of EP1851498A1 publication Critical patent/EP1851498A1/fr
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Publication of EP1851498B1 publication Critical patent/EP1851498B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F28F1/34—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 obliquely
    • F28F1/36—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 obliquely the means being helically wound fins or wire spirals
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • 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

Definitions

  • the invention relates to the field of tubes for heat exchangers, and more particularly the field of heat exchangers operating in evaporation / condensation and in reversible mode.
  • the invention relates to the use of heat exchangers defined in claim 1.
  • Japanese demand no. 57-58088 discloses V-grooved tubes, with H between 0.02 and 0.2 mm, and with an angle ⁇ between 4 and 15 °. Neighboring tubes are described in Japanese Application No. 57-58094 .
  • Japanese demand no. 52-38663 discloses tubes with V or U grooves, with H between 0.02 and 0.2 mm, a pitch P between 0.1 and 0.5 mm and an angle ⁇ between 4 and 15 °.
  • the patent U.S. 4,044,797 describes grooved tubes in V or U adjacent to the preceding tubes.
  • Japanese utility model no. 55-180186 describes tubes with trapezoidal grooves and triangular ribs, with a height H of 0.15 to 0.25 mm, a pitch P of 0.56 mm, an apex angle ⁇ (angle called ⁇ in this document) typically equal to 73 °, an angle ⁇ of 30 °, and an average thickness of 0.44 mm.
  • Licences U.S. Patent No. 4,545,428 and no 4480684 describe tubes with V-grooves and triangular ribs, with the height H between 0.1 and 0.6 mm, a pitch P between 0.2 and 0.6 mm, an apex angle ⁇ of between 50 and 100 °, a helix angle ⁇ between 16 and 35 °.
  • Japanese Patent No. 62-25959 describes tubes with trapezoidal grooves and ribs, with a groove depth H of between 0.2 and 0.5 mm, a pitch P of between 0.3 and 1.5 mm, the average width of the grooves being at least equal to the average width of the ribs.
  • the pitch P is 0.70 mm and the helix angle ⁇ is 10 °.
  • the European patent EP-B1-701 680 in the name of the applicant, describes grooved tubes, with grooves typically flat bottom and with ribs of different height H, helix angle ⁇ between 5 and 50 °, apex angle ⁇ between 30 and 60 °, to obtain better performances after the crimping of the tubes and assembly in the exchangers.
  • the object of the present invention relates to the use of tubes for reversible heat exchangers, that is to say a use where tubes or exchangers are used with refrigerants with change of applications.
  • phase sometimes in evaporation, sometimes in condensation, that is to say either to cool, for example as air conditioners, or to heat, for example as heating means, typically air or a secondary fluid.
  • the present invention relates to the use of tubes which not only have an excellent compromise between thermal performance in evaporative and refrigerant condensation mode, but which, moreover, intrinsically have high performance as well. in evaporation only in condensation.
  • the applicant has therefore sought economic tubes and exchangers, with a relatively low weight per meter, and high heat exchange performance, both in evaporation and in condensation.
  • the characteristic defined under a) defines the outer diameter range of tubes in the range of application targeted by the tubes according to the invention.
  • the characteristic under d), relative to the apex angle ⁇ , provides that this angle must be chosen in a relatively narrow range (20 ° - 28 °) and with relatively low ⁇ -apex angle values.
  • a low ⁇ -angle value is preferable for improving the heat transfer performance to decrease the pressure drop and to decrease the weight of the tube / m. It is with trapezoidal ribs that the angle ⁇ may be the weakest.
  • the lower limit is essentially related to the manufacture of grooved tubes according to the invention to maintain a high rate of production.
  • the thickness Tf of the tube at the bottom of the groove may vary according to the diameter De, so as to have both sufficient mechanical properties, including resistance to internal pressure, a maximum saving in material, and therefore optimized material cost, and a weight per meter as low as possible.
  • This thickness Tf is 0.28 mm for a 9.55 mm diameter tube De, and 0.35 mm for a tube 12.7 mm in diameter De.
  • the different curves of the figure 4 give, in condensation at 30 ° C with fluid R22, the exchange coefficient Hi (in W / m 2 .K) in ordinate as a function of the fluid flow G, in abscissa (in Kg / m 2 .s).
  • the different curves of the figure 5 give, in evaporation at 0 ° C of the fluid R22, the exchange coefficient Hi (in W / m 2 .K) in ordinate as a function of the fluid flow G, in abscissa (in Kg / m 2 .s).
  • the Figures 6 and 7 indicate, on the ordinate, the exchange refrigeration power measured in watts of a battery of tubes and fins as a function, on the abscissa of the frontal velocity of the air which circulates between the fins expressed in m / s.
  • the figure 6 is relative to the condensation measurements on the same battery as before, with an air inlet temperature of 23.5 ° C and a condensing temperature of 36 ° C of the refrigerant R22.
  • the figure 7 is relative to the evaporation measurements on the same battery, with an inlet temperature of 26.5 ° C, and an evaporation temperature of 6 ° C of the refrigerant R22.
  • the figure 8 is a schematic perspective view of the battery (4) of tubes (1) with fins (5) used for testing.
  • the figure 9 graphically represents on the ordinate the cooling capacity gain in evaporation of the batteries, according to the figure 7 , with a reference air speed of 1.25 m / s, as a function of the Cavallini factor on the abscissa for the various tubes tested: smooth tube S, tube E according to the invention, and tubes A and B according to FIG. state of the art.
  • the figure 10 is a graph indicating, on the ordinate, the heat exchange coefficient Hi (W / m 2 .K) on evaporation tubes with the refrigerant R407C, as a function of the weight percentage of vapor in the refrigerant, on the abscissa, the temperature evaporation rate of 5 ° C.
  • the measurements were made with a heat flux of 12 kW / m 2 and a mass flow rate of 100 or 200 kg / m 2 .s of refrigerant R407C, as shown in the figure, on tubes of diameter D equal to 9 52mm.
  • the figure 11 is a view of an inner surface portion of a grooved tube according to the invention provided with an axial counter-groove (30), with, below, its schematic representation.
  • said succession may be an alternation of ribs of height H1 and ribs of height H2 separated by a generally flat groove bottom.
  • the grooved tubes according to the invention do not necessarily include such an alternation of differentially height ribs as on the Figures 2a to 2c , the ribs may have substantially the same height.
  • a range according to the invention of the apex angle ⁇ ranges from 20 ° to 28 °, an even more restricted range from 22 ° to 25 ° ensuring the best compromise. between the technical performance requirements and those related to the expansion of the tubes for attachment to the fins of the batteries.
  • a preferred range of the helix angle ⁇ can range from 22 ° to 30 °, a still more restricted range from 25 ° to 28 ° ensuring the best compromise between technical performance requirements and those related to pressure drop.
  • This angle can vary with the inner diameter Di: it has been found advantageous to have a ⁇ / Di ratio greater than 2.40 ° / mm, and preferably greater than 3 ° / mm.
  • said ribs have a "trapezium" type profile with a base of width L N and a vertex, connected by lateral edges forming between them said apex angle ⁇ , as illustrated in FIG. Figure 2c said apex comprising a substantially flat central portion, typically parallel to said base, but possibly sloping with respect to said base.
  • said vertex of said rib forming a short side of the trapezium may have rounded edges or not, that is to say, very small radius of curvature, these edges forming a connection of said vertex audits side edges.
  • Said rounded edges may have a radius of curvature typically ranging from 40 .mu.m to 100 .mu.m, and preferably ranging from 50 .mu.m to 80 .mu.m, as illustrated in FIGS. Figures 2a to 2c .
  • These ranges of radius of curvature correspond to a compromise between the thermal performance of the tubes and the feasibility of the tubes, the tools for making the tubes with the smallest radii of curvature having the most tendency to wear out.
  • the radius of: curvature can be typically less than 50 microns, and even less than 20 microns.
  • said ribs and said flat bottom of said grooves may be connected with a radius of curvature less than 50 microns, and preferably less than 20 microns. In this case, it seems that there is better separation of the liquid refrigerant film from the inner wall of the tube, which promotes heat exchange.
  • the tubes used according to the invention have even in the absence of axial grooving, a Cavallini factor of at least 3.5. They may advantageously have a Cavallini factor of at least 4.0.
  • the tubes according to the invention may further comprise an axial groove (30) creating in said ribs notches with a typically triangular profile with a rounded top, said top having an angle ⁇ ranging from 25 to 65 °, said lower part or top is at a distance h from the bottom of said grooves from 0 to 0.2 mm.
  • Such axial grooving can be obtained once formed said ribs by passage of a grooving wheel in the axial direction.
  • the grooved tubes according to the invention may be made of copper and alloys of copper, aluminum and aluminum alloys. These tubes can be obtained typically by grooving tubes, or possibly by flat grooving of a metal strip and forming a welded tube.
  • the tests were carried out on copper tubes of 8.0 mm or 9.52 mm of external diameter.
  • the "E” tube of the invention was manufactured according to the Figures 2a to 2c with a diameter of 8.0 mm, and according to the figure 3 with a diameter of 9.52 mm, as well as comparative "S” or smooth, "C", “D”, tubes which have a high ⁇ helix angle (at least equal to 20 °), intended for the condensation according to the state of the art, and comparative tubes "A” and “B”, which have a high apex angle ⁇ (at least equal to 40 °) and a low helix angle ⁇ (at most equal at 18 °), intended for evaporation according to the state of the art.
  • the tubes E, A, B, C were made by grooving a smooth copper tube - S tube, while the D tube was manufactured by flat grooving a metal band and then forming a welded tube.
  • Tube type H in mm angle ⁇ angle ⁇ NOT Rib type Tf mm L R / L N E Fig.3 0.20 25 25 66 V 0.30 2.3 B from 0.20 to 0.17 40 16 74 Alternating triangles 0.30 1.88 AT 0.20 50 18 60 triangular 0.30 2.00 VS 0.20 40 30 60 triangular 0.30 1.94 D 0.20 15 20 72 Double crossed ribs * 0.30 3.66 s ------- ------- ------- -- -- -- -- -- Smooth tube 0.30 ------- * 72 main ribs of helix angle ⁇ equal to + 20 ° interspersed with secondary grooves inclined at an angle of -20 ° relative to the axis of the tube, the depth of the grooves being substantially equal to the height of the ribs main.
  • Winged batteries were manufactured according to the figure 8 from these tubes, placing the tubes in the flanges of the fins and then pressing the tube against the flange of the flanges by expansion of the tube with a conical mandrel.
  • These batteries form a block of dimensions: 400 mm x 400 mm x 65 mm, with a density of 12 fins per 25.4 mm, the battery comprising 3 rows of 16 tubes, and the refrigerant being the R22.
  • the tubes and exchangers or batteries of tubes according to the invention have properties superior to the analogous products of the state of the art, both in evaporation and in condensation.
  • the tubes according to the invention do not only constitute a good compromise of performance in evaporation and condensation, but also have, in absolute terms, excellent performance compared to the tubes of the state. of the technique used in evaporation and those used in condensation, which is of great interest in practice.
  • the values obtained with the tubes according to the invention correspond to a gain ranging from 3.7 to 6.7% compared to the tubes according to the state of the art, taken from same diameter and same thickness Tf, which is considered very important.
  • the tubes according to the invention of the type E can be advantageously manufactured by high-speed grooving of smooth non-grooved copper tube, typically at a grooving speed close to that used for the type B tubes, namely at least 80 m / min.
  • the invention has great advantages. Indeed, on the one hand, the tubes and batteries used according to the invention have high intrinsic performances. On the other hand, these performances are high in both evaporation and condensation, which allows the use of the same tube for these two applications. In addition, the tubes have a relatively low weight per meter, which is very advantageous both from a practical point of view and from the economic point of view with a relatively low material cost.
  • tubes used according to the invention do not require specific manufacturing means. They can be manufactured with standard equipment and especially with the usual production rates.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)
  • Lining Or Joining Of Plastics Or The Like (AREA)
  • Treatment Of Fiber Materials (AREA)
EP03743918.9A 2002-03-12 2003-03-10 Tubes rainures a utilisation reversible pour echangeurs thermiques Expired - Lifetime EP1851498B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0203067A FR2837270B1 (fr) 2002-03-12 2002-03-12 Tubes rainures a utilisation reversible pour echangeurs thermiques
PCT/FR2003/000760 WO2003076861A1 (fr) 2002-03-12 2003-03-10 Tubes rainures a utilisation reversible pour echangeurs thermiques

Publications (2)

Publication Number Publication Date
EP1851498A1 EP1851498A1 (fr) 2007-11-07
EP1851498B1 true EP1851498B1 (fr) 2013-05-15

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EP03743918.9A Expired - Lifetime EP1851498B1 (fr) 2002-03-12 2003-03-10 Tubes rainures a utilisation reversible pour echangeurs thermiques

Country Status (21)

Country Link
US (1) US7048043B2 (ko)
EP (1) EP1851498B1 (ko)
JP (1) JP2005526945A (ko)
KR (1) KR100980755B1 (ko)
CN (1) CN1636128A (ko)
AU (1) AU2003242811B2 (ko)
BR (1) BR0308372A (ko)
CA (1) CA2474558C (ko)
ES (1) ES2449091T3 (ko)
FR (1) FR2837270B1 (ko)
HR (1) HRP20040819B1 (ko)
IL (2) IL162942A0 (ko)
MX (1) MXPA04007907A (ko)
MY (1) MY135526A (ko)
NO (1) NO338468B1 (ko)
PL (1) PL201843B1 (ko)
PT (1) PT1851498E (ko)
RU (1) RU2289076C2 (ko)
WO (1) WO2003076861A1 (ko)
YU (2) YU76804A (ko)
ZA (1) ZA200405864B (ko)

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FR2837270B1 (fr) 2002-03-12 2004-10-01 Trefimetaux Tubes rainures a utilisation reversible pour echangeurs thermiques

Also Published As

Publication number Publication date
NO20044299L (no) 2004-10-11
BR0308372A (pt) 2005-01-11
PT1851498E (pt) 2013-07-04
RU2289076C2 (ru) 2006-12-10
FR2837270A1 (fr) 2003-09-19
JP2005526945A (ja) 2005-09-08
NO338468B1 (no) 2016-08-22
US20030173071A1 (en) 2003-09-18
AU2003242811B2 (en) 2009-05-28
IL162942A0 (en) 2005-11-20
RU2004130315A (ru) 2005-06-10
HRP20040819B1 (hr) 2017-12-01
IL162942A (en) 2008-06-05
CA2474558A1 (en) 2003-09-18
EP1851498A1 (fr) 2007-11-07
WO2003076861A1 (fr) 2003-09-18
PL201843B1 (pl) 2009-05-29
KR20040101283A (ko) 2004-12-02
CA2474558C (en) 2011-03-08
CN1636128A (zh) 2005-07-06
YU101804A (sh) 2006-01-16
KR100980755B1 (ko) 2010-09-07
HRP20040819A2 (en) 2004-12-31
AU2003242811A1 (en) 2003-09-22
FR2837270B1 (fr) 2004-10-01
MXPA04007907A (es) 2004-10-15
PL370690A1 (en) 2005-05-30
ES2449091T3 (es) 2014-03-18
ZA200405864B (en) 2005-06-21
MY135526A (en) 2008-05-30
YU76804A (sh) 2006-01-16
US7048043B2 (en) 2006-05-23

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