US20160341491A1 - Improved tube for a heat exchanger - Google Patents

Improved tube for a heat exchanger Download PDF

Info

Publication number
US20160341491A1
US20160341491A1 US15/109,239 US201515109239A US2016341491A1 US 20160341491 A1 US20160341491 A1 US 20160341491A1 US 201515109239 A US201515109239 A US 201515109239A US 2016341491 A1 US2016341491 A1 US 2016341491A1
Authority
US
United States
Prior art keywords
segment
tubes
element according
wall
millimeters
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
US15/109,239
Other languages
English (en)
Inventor
Joël DUPRAT
Pascal SAUSSIER
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.)
Neotiss SAS
Original Assignee
Neotiss SAS
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 Neotiss SAS filed Critical Neotiss SAS
Assigned to VALLOUREC HEAT EXCHANGER TUBES reassignment VALLOUREC HEAT EXCHANGER TUBES ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DUPRAT, JOEL, SAUSSIER, Pascal
Assigned to NEOTISS SAS reassignment NEOTISS SAS CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: VALLOUREC HEAT EXCHANGER TUBES
Publication of US20160341491A1 publication Critical patent/US20160341491A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid as the cooling medium
    • 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
    • F28D7/103—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 more than two coaxial conduits or modules of more than two coaxial conduits
    • 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
    • F28D7/16—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 in parallel spaced relation
    • 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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
    • F28D2021/0063—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
    • F28F2210/00—Heat exchange conduits
    • F28F2210/06—Heat exchange conduits having walls comprising obliquely extending corrugations, e.g. in the form of threads

Definitions

  • the invention relates to an element for a heat exchanger of industrial type, in particular a condenser, of the type comprising a generally tubular body.
  • Condensers comprising such elements, also known as “tube condensers” are widely used in industry, in particular for electricity production.
  • a first fluid typically water in the liquid state
  • a second fluid in the gaseous state generally steam
  • Heat is then exchanged between the first and second fluids, through the wall of the tubes, which exchange causes the fluid in the gaseous state to condense.
  • Condensers of the industrial type must be able to condense large quantities of steam in as short a time as possible.
  • the volume of steam that they are capable of condensing per unit of time at least partly characterises their performance.
  • condensers of the industrial type are generally fitted with hundreds, or even thousands, of great-length tubes, typically up to around twenty metres long.
  • tubes of a new type started to be used, the body of which still retains its generally tubular shape, but the wall of which has a twisted shape extending over at least one segment of said body. This twisted shape of the wall results in an outer surface with a domed relief extending helically along the segment in question, and a corresponding groove on the inner surface of the body.
  • the twisted shape significantly improves the heat exchanges at the tubes: on the one hand, the twisted shape gives the wall a larger contact area between the fluids, both on the inside and the outside of the tubes; on the other hand, it causes turbulence in the fluid flowing inside the tubes, which is beneficial overall for the heat exchanges at the tubes.
  • the twisted shape also improves the drainage of the drops that form on the outer surface of the tubes.
  • tubes with this type of configuration are known as “corrugated” or, more correctly, “equipped with corrugations”.
  • the pitch of the twist also known as the corrugation pitch, is generally greater than 20 millimetres.
  • the invention aims to improve the existing situation.
  • the proposed heat exchanger element comprises a tubular body the wall of which is at least partly delimited by an inner surface and an outer surface.
  • the wall has a twisted shape on at least one segment of said body.
  • the inner surface has at least one groove with a shape corresponding to said wall that extends helically over said segment.
  • the outer surface has a diameter comprised between 18 and 30 millimetres, while the groove has a pitch of less than 3.5 millimetres and a depth such that the ratio of the pitch at a real power comprised between 1.5 and 2.5 to the depth is less than a threshold value close to 24.
  • FIG. 1 shows a diagram of a generic heat exchanger
  • FIG. 2 is a top view of a tube element for the exchanger in FIG. 1 ;
  • FIG. 3 is a longitudinal cross-sectional view of a wall portion of a tube element for the exchanger in FIG. 1 ;
  • FIG. 4 shows a partially cut away perspective view of a twisted portion of a tube element for a heat exchanger.
  • FIG. 1 It shows, generically, a heat exchanger of industrial type in the form of a condenser 1 .
  • the condenser 1 comprises a plurality of individual tubes 3 held in relation to each other in one or more bundles 5 by plates 7 distributed along the tubes 3 . Each plate 7 is thus passed through by each of the tubes 3 in the bundle 5 .
  • the condenser 1 also comprises a pair of header tanks 9 into which the opposite ends of each of the tubes 3 respectively open out.
  • One of the tanks 9 is in fluid communication with a fluid inlet 11 , while the other tank 9 is in fluid communication with a fluid outlet 13 .
  • the inlet 11 and outlet 13 can be connected to the rest of a circuit in which a first fluid circulates.
  • the first fluid enters the condenser 1 through the inlet 11 in liquid form. It circulates from the corresponding header tank 9 to the other header tank inside the tubes 3 in one or more passes. From there, the first fluid leaves the condenser 1 for the rest of the circuit through the outlet 13 .
  • the bundle 5 of tubes 3 is housed in an enclosure 15 provided inside what is known in the art as a shell 17 .
  • the shell 17 is equipped with a fluid inlet 19 and a fluid outlet 21 that open out into the enclosure 15 .
  • the inlet 19 and outlet 21 allow the condenser 1 to be connected to a circuit in which a second fluid circulates.
  • the second fluid enters the enclosure 15 through the inlet 19 in gaseous form.
  • the second fluid exchanges heat with the first fluid circulating inside these tubes.
  • the first fluid is generally introduced at a lower temperature than that of the second fluid, the latter condenses on the outer surface of the tubes 3 .
  • the second fluid in liquid form leaves the enclosure 15 through the outlet 21 .
  • Condensers of the type of the condenser 1 are widely used in industrial electricity production.
  • steam is condensed by means of cold water circulating inside the tubes.
  • great-length tubes each up to around twenty metres long are used.
  • FIG. 2 It shows a tube element TE that can be used in a condenser of the type of the condenser 1 .
  • the tube element TE comprises a hollow elongated generally cylindrical, or tubular, body BDY with a length TL.
  • the body BDY has two longitudinal end sections ES 1 and ES 2 connected to each other by a central section CS with a length CL.
  • the length TL corresponds to the total length of the tubular element TE, including the central section CS and the end sections ES 1 and ES 2 .
  • the end sections ES 1 and ES 2 are generally cylindrical, with an outside diameter TOD.
  • the diameter TOD corresponds to the nominal outside diameter of the element TE.
  • the end sections ES 1 and ES 2 each have a smooth outer and inner surface.
  • the central section CS has a wall that extends along the body in a twist, or helically, or in a helix, forming spirals LP around the longitudinal axis LA of the tube element TE.
  • the spirals LP are contiguous.
  • This twisted configuration of the wall of the element TE results in an outer surface that, over the length of the central section CS, has a helical relief, made of hollows and bosses.
  • This relief is likely to improve the heat exchange capabilities of the element TE, because the outer surface thereof is then more extensive than that of a smooth tube with the same outside diameter. Furthermore, it improves the drainage of the drops that form on the outer surface of the element TE.
  • the central section CS retains the general appearance of a hollow cylinder, having an outside diameter COD.
  • FIGS. 3 and 4 show, generically, a twisted portion CW of the wall and a configuration of said twisted shape.
  • the twisted shape of the wall CW results in an inner surface IS with a relief made of peaks and hollows, with a shape corresponding respectively to the hollows and bosses on the outer surface OS.
  • the inner surface IS has a groove that extends along a helix with contiguous spirals along the central section CS.
  • the inner surface IS has a helical shape.
  • This relief is likely to improve the heat exchange capabilities of the element TE, due to the generation of eddies in the fluid flowing inside the element TE.
  • the twisted wall CW has a thickness TT.
  • the thickness TT corresponds to the nominal thickness of the element TE, i.e. the thickness of the wall of the smooth tube on which the element TE is based.
  • the central section CS has an inside diameter CID.
  • the diameter CID corresponds to the diameter of a gauge just capable of passing through the inside of the element TE.
  • the twisted section CS has an outside diameter COD that corresponds to the nominal outside diameter of the element TE on the twisted section CS, i.e. the diameter of a cylindrical envelope surface of said section.
  • the twisted shape has a pitch CP, if applicable considered inside the tubular element.
  • the depth CD of the inner groove resulting from the twisted shape is considered in relation to an inner envelope surface of the tubular element or, in other words, as the radial distance between the bottom of the hollows in the inner surface IS and the summit of the peaks.
  • the dimension corresponding to the nominal inside diameter of the tube can be denoted TED, as it is usually known in the art, i.e. here, the nominal inside diameter of the smooth end sections ES 1 and ES 2 .
  • the tube element TE has, on the twisted section CS, a nominal outside diameter COD comprised between 18 and 30 millimetres.
  • the pitch CP of the twist is less than 3.5 millimetres.
  • the depth CD is such that the ratio of the pitch CP raised to a real power R comprised between 1.5 and 2.5 to the depth CD, which is known as the form ratio FR, remains less than a threshold value TV.
  • the threshold value TV is close to 24.
  • the power R is close to 1.7.
  • the depth CD verifies the conditions COND1, COND2 and COND3 set out below:
  • Variant 1 Variant 2 Variant 3 TOD 19.05 22.22 25.40 COD 18.90 22.07 25.25 TT 0.5 0.5 0.5 CP between 2 and 3.5 between 2 and 3.5 between 2 and 3.5 CD between 0.15 and between 0.15 and between 0.2 and 0.3 0.3 0.3 0.3
  • Embodiment 1 Embodiment 2 TOD 19.05 22.22 COD 18.90 22.07 TT 0.5 0.5 CP 2 2.5 CD 0.16 0.25
  • Tables 1A and 1B show that the twisted part of the tubes according to the invention has a very small pitch, less than 3.5 millimetres, and preferably less than 3 millimetres, compared with the pitch values conventionally used in corrugated tubes, which are typically greater than 20 millimetres.
  • the tubes according to the invention therefore differ from conventional tubes in that the twisted section has a shape that resembles a spiral.
  • Table 2 below shows dimensional characteristics relating to a set of tube elements (marked I, . . . , XII) each with a twisted central section.
  • the tube elements differ from each other in the profile of the respective twisted section thereof, characterised by pitch CP and depth CD values that differ from each other.
  • Dimensions absent from Table 2 are common to the tubes I to XIV.
  • the tube elements all have an outside diameter of 22.22 millimetres and a wall thickness of 0.5 millimetre.
  • the tubes are made from grade 2 titanium.
  • the pitch CP and depth CD values are expressed in millimetres.
  • Table 2 also shows the corresponding values of the form ratio FR, calculated for a power R value of 1.7.
  • tube elements II and III are according to variant 2 .
  • Tube element III is also according to embodiment 2.
  • elements I, II, III, V and VIII are according to the invention in that they have pitch values CP of less than 3.5 millimetres and also verify conditions COND1, COND2 and COND3.
  • Tube elements IV and VI have dimensions according to variant 2 , with the exception that they do not verify conditions COND1 to COND3.
  • Table 3 below shows the results of heat exchange capacity measurements taken on the elements in Table 2.
  • the coefficient K represents a heat exchange capacity measured for the tube element in question.
  • the coefficient K is expressed in Watt per square metre Kelvin (W ⁇ m ⁇ 2 ⁇ K ⁇ 1 ).
  • the HER value expressed as a percentage, corresponds to the improvement in the value of K for the element in question compared with a smooth element with otherwise similar dimensions.
  • Table 3 shows that compliance with conditions COND1, COND2 and COND3 is generally associated with a significant increase in heat exchange performance.
  • the rows corresponding to tube elements I, II, III, V, VIII, X and XII have coefficient K values at least 45% greater than the reference value for a smooth tube (5,272 W ⁇ m ⁇ 2 ⁇ K ⁇ 1 ).
  • a comparison in Table 2 of rows VII and X on one hand, and rows I, XIII and XIV on the other hand also shows a slight increase in heat exchange performance when the ratio FR exceeds the threshold value of 24. When the ratio FR is greater than the threshold value, the increase in heat exchange performance compared with a smooth tube is generally less than 30%.
  • Table 3 proves that the tube elements according to the invention have greatly improved heat transfer capabilities compared with smooth elements on the one hand, and elements the twisted section of which departs from the profile provided for by the invention.
  • Table 4 below shows the results of measurements taken on the tube elements in Table 2.
  • Table 4 also shows the values of the coefficient known as the Darcy or Darcy-Weisbach coefficient, for the tubes in question, as well as the increase DCR in the value of this coefficient compared with a smooth reference tube.
  • the Darcy coefficient corresponds to a head loss coefficient. This dimensionless quantity represents the influence of the type of flow (laminar or turbulent) and the finish of a pipe (smooth or rough) on the head loss.
  • the Darcy coefficient is calculated for a flow rate of 2.5 cubic metres per hour.
  • An increase in the Darcy value is overall unfavourable to the performance of a tube element within a condenser.
  • an increase in the Darcy value implies an increase in the energy consumption required for the circulation of the fluid inside the tubes.
  • the increase in the Darcy value is detrimental to the condensation of the steam on the outside of the tube element for the same energy consumption.
  • Table 4 shows in general terms that the tubes according to the invention have a significant increase in Darcy value. However, this increase remains limited (less than 140 and lower than for certain tubes not according to the invention, as shown by a comparison with rows X and XII). Furthermore, the relative increase in the Darcy coefficient is very small (close to, or even less than 100%) for the elements according to the second variant (tubes II and III) and for tube I, compared with the other tubes tested. The tubes of the second variant and tube I have an increase in the Darcy value that is markedly less than for the others.
  • the tubes with a twisted section according to the invention are capable of greatly improved performance regarding their capacity to condense a gas circulating outside the tube.
  • This improved performance results from a twisted shape that greatly improves the heat exchange capabilities and substantially limits the head loss effects.
  • the tubes according to variants 1 to 3 and embodiments 1 and 2 are capable of showing condensation performance that is further improved due to heat exchange capabilities comparable to the other tubes according to the invention and substantially lower head losses compared with these tubes.
  • the outside diameter of the tube TOD is between 19 and 26 millimetres, preferably between 20 and 26 millimetres, and even more preferentially between 20 and 23 millimetres. In particular, the outside diameter TOD is close to 19.05 millimetres, 22.22 millimetres or 25.4 millimetres.
  • the outside diameter COD of the twisted part is between 18 and 26 millimetres, preferably between 20 and 26 millimetres, and even more preferentially between 20 and 23 millimetres. In particular, the outside diameter COD is close to 18.90 millimetres, 22.07 millimetres or 25.25 millimetres.
  • the pitch CP is strictly greater than 2 millimetres. It is less than 3 millimetres.
  • the depth CD is comprised between 0.05 and 0.6 millimetres, in particular greater than 0.15 millimetres.
  • the thickness TT of the wall CW of the tube is between 0.4 and 1 millimetre, for example of the order of 0.5 millimetre.
  • the invention is not limited to the embodiments described above, but encompasses all of the variants that a person skilled in the art might imagine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US15/109,239 2014-01-20 2015-01-19 Improved tube for a heat exchanger Abandoned US20160341491A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR1450439 2014-01-20
FR1450439A FR3016689B1 (fr) 2014-01-20 2014-01-20 Tube ameliore pour echangeur thermique
PCT/FR2015/050126 WO2015107314A1 (fr) 2014-01-20 2015-01-19 Tube amélioré pour échangeur thermique

Publications (1)

Publication Number Publication Date
US20160341491A1 true US20160341491A1 (en) 2016-11-24

Family

ID=50624760

Family Applications (1)

Application Number Title Priority Date Filing Date
US15/109,239 Abandoned US20160341491A1 (en) 2014-01-20 2015-01-19 Improved tube for a heat exchanger

Country Status (8)

Country Link
US (1) US20160341491A1 (ko)
EP (1) EP3097377B1 (ko)
JP (1) JP6648036B2 (ko)
KR (1) KR20160121537A (ko)
CN (1) CN106104190A (ko)
FR (1) FR3016689B1 (ko)
RU (1) RU2016129630A (ko)
WO (1) WO2015107314A1 (ko)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170328641A1 (en) * 2017-02-28 2017-11-16 Zhengzhou University Shell-and-tube heat exchanger with externally-connected tube chambers
US20170328642A1 (en) * 2017-02-28 2017-11-16 Zhengzhou University Shell-and-tube heat exchanger with distributed inlet-outlets
US11493282B2 (en) * 2016-08-05 2022-11-08 Obshestvo S Ogranichennoi Otvetstvennost'u “Reinnolts Lab” Shell and tube condenser and the heat exchange tube of a shell and tube condenser (variants)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3147619A1 (de) * 2015-09-28 2017-03-29 Siemens Aktiengesellschaft Rohre für kraftwerkskondensatoren

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3826304A (en) * 1967-10-11 1974-07-30 Universal Oil Prod Co Advantageous configuration of tubing for internal boiling
US3841136A (en) * 1972-03-07 1974-10-15 Universal Oil Prod Co Method of designing internally ridged heat transfer tube for optimum performance
JPH02242091A (ja) * 1989-03-16 1990-09-26 Sanyo Electric Co Ltd 液―液式熱交換器用伝熱管
US5680772A (en) * 1995-11-29 1997-10-28 Sanyo Electric Co., Ltd. Absorption type refrigerating machine
US5996686A (en) * 1996-04-16 1999-12-07 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
US20120011872A1 (en) * 2009-02-27 2012-01-19 Danfoss Commercial Compressors Device for separating lubricant from a lubricant-refrigerating gas mixture discharged from at least one refrigerant compressor
US8387684B2 (en) * 2007-07-11 2013-03-05 Visteon Global Technologies, Inc. Exhaust gas heat exchanger with an oscillationattenuated bundle of exchanger tubes

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3217799A (en) * 1962-03-26 1965-11-16 Calumet & Hecla Steam condenser of the water tube type
GB1267149A (en) * 1970-06-01 1972-03-15 Universal Oil Prod Co Heat transfer tube with porous boiling-surface
DE3010450A1 (de) * 1980-03-19 1981-09-24 Kabel- und Metallwerke Gutehoffnungshütte AG, 3000 Hannover Rohr fuer waermetauscherzwecke, insbesondere fuer verdampfer
US5690167A (en) * 1994-12-05 1997-11-25 High Performance Tube, Inc. Inner ribbed tube of hard metal and method
EP1793188A1 (en) * 2005-12-05 2007-06-06 GEA Ibérica S.A. Surface condenser
CN1924507A (zh) * 2006-09-08 2007-03-07 清华大学 用于热水器的螺旋槽换热管
CN201034436Y (zh) * 2007-03-27 2008-03-12 高克联管件(上海)有限公司 双重强化的蒸发用传热管
JP4420117B2 (ja) * 2008-01-28 2010-02-24 日立電線株式会社 熱交換器用伝熱管及びこれを用いた熱交換器
CN201289332Y (zh) * 2008-09-27 2009-08-12 山东亿佳美暖通设备有限公司 不锈钢螺纹管
KR101620106B1 (ko) * 2010-01-15 2016-05-13 엘지전자 주식회사 이중 열교환기

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3826304A (en) * 1967-10-11 1974-07-30 Universal Oil Prod Co Advantageous configuration of tubing for internal boiling
US3841136A (en) * 1972-03-07 1974-10-15 Universal Oil Prod Co Method of designing internally ridged heat transfer tube for optimum performance
JPH02242091A (ja) * 1989-03-16 1990-09-26 Sanyo Electric Co Ltd 液―液式熱交換器用伝熱管
US5680772A (en) * 1995-11-29 1997-10-28 Sanyo Electric Co., Ltd. Absorption type refrigerating machine
US5996686A (en) * 1996-04-16 1999-12-07 Wolverine Tube, Inc. Heat transfer tubes and methods of fabrication thereof
US8387684B2 (en) * 2007-07-11 2013-03-05 Visteon Global Technologies, Inc. Exhaust gas heat exchanger with an oscillationattenuated bundle of exchanger tubes
US20120011872A1 (en) * 2009-02-27 2012-01-19 Danfoss Commercial Compressors Device for separating lubricant from a lubricant-refrigerating gas mixture discharged from at least one refrigerant compressor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11493282B2 (en) * 2016-08-05 2022-11-08 Obshestvo S Ogranichennoi Otvetstvennost'u “Reinnolts Lab” Shell and tube condenser and the heat exchange tube of a shell and tube condenser (variants)
US20170328641A1 (en) * 2017-02-28 2017-11-16 Zhengzhou University Shell-and-tube heat exchanger with externally-connected tube chambers
US20170328642A1 (en) * 2017-02-28 2017-11-16 Zhengzhou University Shell-and-tube heat exchanger with distributed inlet-outlets

Also Published As

Publication number Publication date
FR3016689B1 (fr) 2016-01-15
JP2017503146A (ja) 2017-01-26
CN106104190A (zh) 2016-11-09
EP3097377B1 (fr) 2022-04-20
WO2015107314A1 (fr) 2015-07-23
FR3016689A1 (fr) 2015-07-24
JP6648036B2 (ja) 2020-02-14
EP3097377A1 (fr) 2016-11-30
RU2016129630A (ru) 2018-01-25
KR20160121537A (ko) 2016-10-19

Similar Documents

Publication Publication Date Title
US20160341491A1 (en) Improved tube for a heat exchanger
US20170108279A1 (en) Heat exchanger with multiple flow tubes for fluid circulation
ITBO20120573A1 (it) Scambiatore di calore perfezionato per caldaie a condensazione
CN104848713A (zh) 一种具有多头螺旋槽纹管的换热器
CN104748586A (zh) 一种管壳式换热器
CN201828091U (zh) 一种微通道平行流降膜冷凝器
CN104896985B (zh) 用于空调器的翅片式换热器
US9733024B2 (en) Tubing element with fins for a heat exchanger
CN207540401U (zh) 一种异向翅片管折流管壳式换热器
JP5670672B2 (ja) 熱交換器
KR102025459B1 (ko) 열교환기 수단용 배관 요소
CN102918348B (zh) 热交换器以及使用该热交换器的热泵装置
CN207299987U (zh) 一种管翅壳式换热器
US20200182561A1 (en) Corrugated tube-in-tube heat exchangers
CN205784016U (zh) 一种盘管式蒸发器
CN105987624A (zh) 具有分形结构的列管式换热器
CN205784743U (zh) 一种具有自支撑结构导流装置的换热器
CN214701839U (zh) 一种内凸纹外凹槽螺旋管式换热器
US20210010755A1 (en) Multi-cavity tubes for air-over evaporative heat exchanger
CN219640225U (zh) 盘管结构、热交换组件及热交换器
KR101543522B1 (ko) 열교환기용 납작관 및 이를 구비하는 열교환기
CN219841673U (zh) 一种用于蒸发式冷凝器的盘管
CN219736056U (zh) 一种长管型换热器
CN212431815U (zh) 卧式壳管冷凝器
CN207570371U (zh) 一种螺旋式二次换热装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: VALLOUREC HEAT EXCHANGER TUBES, FRANCE

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:DUPRAT, JOEL;SAUSSIER, PASCAL;REEL/FRAME:039055/0660

Effective date: 20160412

AS Assignment

Owner name: NEOTISS SAS, FRANCE

Free format text: CHANGE OF NAME;ASSIGNOR:VALLOUREC HEAT EXCHANGER TUBES;REEL/FRAME:039826/0158

Effective date: 20160429

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION