EP2253922A2 - Tuyau d'échange thermique métallique - Google Patents

Tuyau d'échange thermique métallique Download PDF

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Publication number
EP2253922A2
EP2253922A2 EP10004200A EP10004200A EP2253922A2 EP 2253922 A2 EP2253922 A2 EP 2253922A2 EP 10004200 A EP10004200 A EP 10004200A EP 10004200 A EP10004200 A EP 10004200A EP 2253922 A2 EP2253922 A2 EP 2253922A2
Authority
EP
European Patent Office
Prior art keywords
rib
boundary surface
tube
heat exchanger
convex
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.)
Granted
Application number
EP10004200A
Other languages
German (de)
English (en)
Other versions
EP2253922A3 (fr
EP2253922B1 (fr
Inventor
Achim Gotterbarm
Jean Dr. El Hajal
Andreas Dr. Beutler
Ronald Lutz
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.)
Wieland Werke AG
Original Assignee
Wieland Werke AG
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 Wieland Werke AG filed Critical Wieland Werke AG
Publication of EP2253922A2 publication Critical patent/EP2253922A2/fr
Publication of EP2253922A3 publication Critical patent/EP2253922A3/fr
Application granted granted Critical
Publication of EP2253922B1 publication Critical patent/EP2253922B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F28F1/40—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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J5/00—Methods for forging, hammering, or pressing; Special equipment or accessories therefor
    • B21J5/06—Methods for forging, hammering, or pressing; Special equipment or accessories therefor for performing particular operations
    • B21J5/068—Shaving, skiving or scarifying for forming lifted portions, e.g. slices or barbs, on the surface of the material
    • 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
    • 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
    • F28F1/26—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 being integral with the 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
    • F28F1/12—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
    • F28F1/42—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
    • 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
    • F28F1/422—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 with outside means integral with the tubular element and inside means integral with 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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the invention relates to a metallic heat exchanger tube according to the preamble of claim 1.
  • Such metallic heat exchanger tubes are used in particular for the condensation of liquids from pure substances or mixtures on the tube outside. Condensation occurs in many areas of refrigeration and air conditioning technology as well as in process and energy technology. Frequently, shell-and-tube heat exchangers are used, in which vapors from pure substances or mixtures are liquefied on the outside of the pipe, thereby heating a brine or water on the inside of the pipe.
  • Such apparatuses are referred to as tube bundle condensers or tube bundle liquefiers.
  • the heat exchanger tubes for shell and tube heat exchangers usually have at least one structured area and smooth end pieces and possibly smooth spacers.
  • the smooth end or intermediate pieces limit the structured areas. So that the tube can be easily installed in the shell and tube heat exchanger, the outer diameter of the structured areas must not be greater than the outer diameter of the smooth end and intermediate pieces.
  • the standard high performance pipes today are about four times more efficient than smooth pipes of the same diameter.
  • ribs are applied to the outer surface of the tube.
  • the surface of the tube is primarily increased and thus the condensation intensified.
  • the ribs are formed from the wall material of the smooth tube, since then there is an optimal contact between the rib and the tube wall.
  • Nippled tubes in which the ribs have been formed from the wall material of a plain tube by means of a forming process are referred to as integrally rolled ribbed tubes.
  • the invention has the object of developing a performance-enhanced heat exchanger tube for the condensation of liquids on the outside of the tube with the same tube-side heat transfer and pressure drop and the same production costs.
  • the mechanical stability of the tube should not be adversely affected.
  • the invention includes a metallic heat exchanger tube having a tube wall and integrally molded ribs on the tube outside which have a rib root, rib flanks and a rib tip, the rib stem projecting substantially radially from the tube wall and the rib flanks provided with additional structural members , which are formed as material projections, which are arranged laterally on the rib side, wherein the material projections have a plurality of boundary surfaces.
  • at least one of the boundary surfaces of at least one material projection is convexly curved.
  • the present invention relates to structured pipes in which the heat transfer coefficient is intensified on the pipe outside.
  • the heat transfer coefficient on the inside usually also needs to be intensified.
  • An increase in the heat transfer on the inside of the pipe usually results in an increase in the pipe-side pressure drop.
  • the integrally rolled finned tube has a tube wall as well as on the outside of the tube helically encircling ribs.
  • the ribs have a ribbed foot, a rib tip and on both sides rib flanks.
  • the rib foot is substantially radially from the pipe wall.
  • the height of the rib is measured from the pipe wall to the fin tip and is preferably between 0.5 and 1.5 mm.
  • the contour of the rib is curved concavely in the radial direction in the region of the rib foot and in the region of the rib flank adjoining the rib base.
  • the contour of the rib is convexly curved in the radial direction.
  • the convex curvature changes into a concave curvature.
  • resulting condensate is pulled away due to surface tension forces. The condensate collects in the area of the concave curvature and forms drops there.
  • the side of the rib flanks additional structural elements in the form of material protrusions are formed.
  • These material protrusions are formed from material of the upper rib flank by means of a Tool the material lifted and displaced similar to a chip, but is not separated from the rib edge.
  • the material projections remain firmly connected to the rib.
  • a concave edge is created between the rib flank and the material projection.
  • the material projections extend substantially in the axial direction of the rib edge in the space between two ribs.
  • the material projections may in particular be arranged approximately at half the height of the ribs. By the material projections, the surface of the tube is increased.
  • the axial extent of the material projections is usually slightly smaller than half the width of the space between two ribs.
  • the width of the gap between two ribs is about 0.4 mm, thus the axial extent of the material protrusions is less than 0.2 mm.
  • the material projections are inventively limited by at least one convex curved surface.
  • the convex shape improves the effect of the additional structural elements. Due to the surface tension, the condensate is drawn away from convexly curved surfaces and towards the concave edge at the point of attachment between the material projection and the rib flank. Therefore, the condensate film on the convexly curved boundary surface of the material projection becomes thinner and the thermal resistance becomes lower.
  • the material projections are arranged approximately in the region of the rib flank, in which the convexly curved contour of the rib merges into the concavely curved contour. Condensate from the top of the rib and condensate from the material projection meet at the point of attachment and form a drop in the concave-shaped part of the rib.
  • the particular advantage is that can be greatly reduced by intensifying the heat transfer on the pipe inside in conjunction with a favorable heat transfer on the pipe outside the size of the condenser. As a result, the production costs of such apparatuses decrease. It is negatively influenced by the inventive solution neither the mechanical stability of a pipe nor the pressure drop.
  • the necessary filling quantity of refrigerant which can account for a not inconsiderable share of the total investment costs in the chlorine-free safety refrigerants that are predominantly used today, is decreasing. In the case of the toxic or flammable refrigerants which are normally only used in special cases, the danger potential can be reduced by reducing the filling quantity.
  • the local radius of curvature of the convex boundary surface can be reduced with increasing distance from the rib edge.
  • a local radius of curvature can be defined as the radius of the nodding circle.
  • the Schmiege Vietnamese lies in a plane perpendicular to the rib side plane. With an arbitrarily shaped boundary surface, this local radius of curvature changes. If such a surface is covered with a liquid film, pressure gradients arise in the liquid film due to the surface tension and the changing radius of curvature. These pressure gradients pull the fluid away from areas of small radius of curvature and toward areas of great radius of curvature.
  • Particularly advantageous embodiments of the material projections are present when the local radius of curvature of its boundary surface with increasing distance from the rib edge gets smaller. The condensate is then pulled away from the areas of the material protrusions, which are remote from the rib flank, particularly efficiently and transported to the rib.
  • the convexly curved boundary surface may be the boundary surface of a material protrusion facing away from the pipe wall.
  • the steam to be condensed can then flow unhindered to this surface.
  • the curvature of the boundary surface may be convexly curved in a plane parallel to the rib flank, wherein the curvature of the convex boundary surface in a plane perpendicular to the rib flank is stronger than the curvature of the convex boundary surface in the plane parallel to the rib side. This additionally promotes the transport of the condensate in the lateral direction from the tip of the material projection to the rib.
  • the radius of an imaginary circle referred to as the mean radius of curvature of the convex boundary surface, can be determined by measurements at three points.
  • the radius of this imaginary circle which lies in a sectional plane perpendicular to the tube circumferential direction and which is defined by the points P1, P2 and P3, be less than 1 mm.
  • P1 is the point where the convex boundary surface of the material protrusion adjoins the rib flank
  • P3 is the point where the convex boundary surface of the material protrusion is farthest from the rib flank
  • P2 is the midpoint between P1 and P3 on the contour line of the convex Boundary surface of the material projection. If this radius of curvature were greater than 1 mm, then the surface tension forces resulting from the commonly used substances, such as refrigerants or hydrocarbons, would not be sufficiently high in gravity relative to the transport of the condensate to influence significantly.
  • the convex boundary surface of the material projection in the region of its tip over the farthest from the rib edge remote point P3 continue with convex curvature.
  • the tip of the material projection is then usually curved helically.
  • additional surface for the condensation is obtained in the available space between the ribs with the same rib spacing.
  • the material protrusions disposed on the rib flank may be circumferentially spaced. This creates additional edges where condensation takes place. Furthermore, the condensate collecting at the rib flank can flow away in the areas between two material projections to the ribbed foot.
  • the material projections arranged on the rib flank can be equidistant in the circumferential direction and spaced at least around their width. As a result, sufficient space for the collecting at the rib side condensate is created to ensure removal.
  • Fig. 1 shows a partial perspective view of a rib portion of a heat exchanger tube 1 with three material projections 4. From the outside of the pipe 21, only a part of the circumferential, integrally molded ribs 3 is shown.
  • the ribs 3 have a rib foot 31, which attaches to the pipe wall, not shown here, rib flanks 32 and a rib tip 33.
  • the rib 3 is substantially radially from the pipe wall.
  • the rib flanks 32 are provided with the additional structural elements, which are formed as material projections 4, which attach laterally to the rib flank 32.
  • These material projections 4 have a plurality of boundary surfaces 41 and 42.
  • the three boundary surfaces 42 of the material projections 4 are convexly curved on the side facing away from the tube wall.
  • another boundary surface 42 or a plurality of boundary surfaces 42 may be provided with a convex curvature.
  • the remaining, non-convex boundary surfaces 41 can either even or concave.
  • the material of the integrally machined material projections 4 originates primarily from the rib flank 32, wherein recesses 34 are formed by a material displacement in the production of the heat exchanger tubes 1.
  • Fig. 2 shows a detailed view of a material projection 4 with a convex curved boundary surface 42.
  • the remaining non-convex boundary surfaces 41 extend flat in this case.
  • the condensate precipitating out of the gas phase is transported away due to the surface tension, as a result of which condensate accumulates increasingly in the area of the concave curvature or even on flat surface areas.
  • the mean radius of curvature RM of the convex boundary surface 42 of an imaginary circle K is defined by the three points P1, P2 and P3.
  • This radius RM can be used as a characterizing measure for the expression of the convex surface.
  • P1 is the point where the convex boundary surface 42 of the material protrusion 4 abuts the rib flank
  • P3 is the point where the convex boundary surface 42 of the material protrusion 4 is farthest from the rib flank
  • P2 is the midpoint between P1 and P3
  • the average radius of curvature RM is typically in the submillimeter range.
  • FIG. 3 A further detail view of a material projection 4 with two opposite convex curved boundary surfaces shows Fig. 3 .
  • a material projection 4 with two opposite convex curved boundary surfaces.
  • all boundary surfaces 42 including the side surfaces 41, have a convex curvature.
  • such embodiments are subject to high process requirements.
  • a further advantageous embodiment can also be in the further detail view in Fig. 4 represented material projection 4 with a doubly convex curved boundary surface 42 and flat side surfaces 41 realize.
  • the curvature of the convex boundary surface in a plane perpendicular to the rib flank is stronger than the curvature of the convex boundary surface 42 in the plane parallel to the rib flank.
  • Such curved surfaces additionally support the condensate drainage towards the rib flank.
  • FIG. 5 shows Fig. 5 in a detailed view of a material projection 4 with flat side surfaces 41 and with a beyond the farthest from the rib edge remote point P3 addition continuing.
  • the tip SP of the material projection 4 is spirally rolled towards the rib foot.
  • additional surface for the condensation is obtained in the available space between the ribs.
  • the mean radius of curvature RM of the convex boundary surface 42 of an imaginary circle K is again defined by the points P1, P2 and P3.
  • Fig. 6 shows a partial perspective view of the outside of a heat exchanger pipe section 1.
  • a further partial perspective view of the inside of a heat exchanger pipe section shows Fig. 7 .
  • the ribs 3 are radially from the pipe wall 2 and are connected via the ribbed 31 with this.
  • material projections 4 are formed, which attach laterally to the rib edge 32.
  • boundary surfaces of the material projections 4 are the from the pipe wall 2 facing away from boundary surfaces 42 convex.
  • the remaining non-convex boundary surfaces 41 are in the embodiment according to Fig. 6 just.
  • Fig. 6 just.
  • the boundary surfaces 41 directed towards the interior of the tube are concave.
  • the material of the integrally machined material projections 4 comes primarily from the rib flank 32 and only partially from the area of the rib tip 33, whereby recesses 34 are formed.
  • the material projections 4 arranged on the rib flank 32 are equidistant in the circumferential direction U approximately at their width. Opposing material projections adjacent ribs 3 do not touch, since the axial extent of the material projections 4 is chosen smaller than half the width of the gap between two ribs 3.
  • Spirally encircling internal ribs 5, which increase the heat transfer to the fluid in the interior of the heat exchanger tube 1 with respect to a smooth tube, are arranged on the inside of the tube 22.
  • Fig. 8 shows a cross-section of a heat exchanger pipe section 1.
  • On the tube inside 22 are spirally encircling inner ribs 5.
  • the ribs 3 on the tube outer side 21 are arranged in a regular sequence starting from the rib foot 31 perpendicular to the tube wall 2, the rib tip 33 is slightly flattened.
  • the facing away from the pipe wall 2 boundary surfaces 42 of the rib edge 32 attaching material projections 4 are convex, the pipe interior 22 directed towards the boundary surfaces 41 are concave. Opposing material projections of adjacent ribs 3 in turn do not touch. As a result, the accumulating condensate sufficient space is created for removal.

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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)
EP10004200.1A 2009-05-14 2010-04-20 Tuyau d'échange thermique métallique Active EP2253922B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009021334A DE102009021334A1 (de) 2009-05-14 2009-05-14 Metallisches Wärmeaustauscherrohr

Publications (3)

Publication Number Publication Date
EP2253922A2 true EP2253922A2 (fr) 2010-11-24
EP2253922A3 EP2253922A3 (fr) 2014-06-11
EP2253922B1 EP2253922B1 (fr) 2016-06-22

Family

ID=42562537

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10004200.1A Active EP2253922B1 (fr) 2009-05-14 2010-04-20 Tuyau d'échange thermique métallique

Country Status (10)

Country Link
US (1) US8550152B2 (fr)
EP (1) EP2253922B1 (fr)
JP (1) JP5748963B2 (fr)
KR (1) KR101892572B1 (fr)
CN (1) CN101886887B (fr)
BR (1) BRPI1001514B1 (fr)
DE (1) DE102009021334A1 (fr)
MX (1) MX2010003434A (fr)
PL (1) PL2253922T3 (fr)
PT (1) PT2253922T (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015128061A1 (fr) * 2014-02-27 2015-09-03 Wieland-Werke Ag Tube d'échangeur de chaleur métallique
EP3581871A1 (fr) * 2018-06-12 2019-12-18 Wieland-Werke AG Tuyau d'échange thermique métallique
WO2022089773A1 (fr) * 2020-10-31 2022-05-05 Wieland-Werke Ag Tube métallique d'échangeur de chaleur
WO2022089772A1 (fr) * 2020-10-31 2022-05-05 Wieland-Werke Ag Tube métallique d'échangeur de chaleur

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011121436A1 (de) 2011-12-16 2013-06-20 Wieland-Werke Ag Verflüssigerrohre mit zusätzlicher Flankenstruktur
CN104251633B (zh) * 2014-04-18 2016-04-20 上海理工大学 扭齿翅片管及其翅片管换热管束
DE102016006914B4 (de) * 2016-06-01 2019-01-24 Wieland-Werke Ag Wärmeübertragerrohr
DE102016006967B4 (de) * 2016-06-01 2018-12-13 Wieland-Werke Ag Wärmeübertragerrohr
US9945618B1 (en) * 2017-01-04 2018-04-17 Wieland Copper Products, Llc Heat transfer surface
KR102275301B1 (ko) * 2019-01-28 2021-07-08 엘지전자 주식회사 전열관 및 칠러용 열교환기

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WO2015128061A1 (fr) * 2014-02-27 2015-09-03 Wieland-Werke Ag Tube d'échangeur de chaleur métallique
US20160305717A1 (en) * 2014-02-27 2016-10-20 Wieland-Werke Ag Metal heat exchanger tube
US11073343B2 (en) 2014-02-27 2021-07-27 Wieland-Werke Ag Metal heat exchanger tube
EP3581871A1 (fr) * 2018-06-12 2019-12-18 Wieland-Werke AG Tuyau d'échange thermique métallique
WO2022089773A1 (fr) * 2020-10-31 2022-05-05 Wieland-Werke Ag Tube métallique d'échangeur de chaleur
WO2022089772A1 (fr) * 2020-10-31 2022-05-05 Wieland-Werke Ag Tube métallique d'échangeur de chaleur

Also Published As

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EP2253922A3 (fr) 2014-06-11
KR101892572B1 (ko) 2018-08-28
EP2253922B1 (fr) 2016-06-22
JP5748963B2 (ja) 2015-07-15
US20100288480A1 (en) 2010-11-18
KR20100123599A (ko) 2010-11-24
DE102009021334A1 (de) 2010-11-18
CN101886887A (zh) 2010-11-17
BRPI1001514A2 (pt) 2011-06-28
JP2010266189A (ja) 2010-11-25
BRPI1001514B1 (pt) 2020-03-03
US8550152B2 (en) 2013-10-08
PL2253922T3 (pl) 2016-12-30
MX2010003434A (es) 2010-11-16
CN101886887B (zh) 2016-01-13
PT2253922T (pt) 2016-09-27

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