EP1739378A1 - Element d'échange de chaleur et échangeur de chaleur associé - Google Patents

Element d'échange de chaleur et échangeur de chaleur associé Download PDF

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Publication number
EP1739378A1
EP1739378A1 EP06011707A EP06011707A EP1739378A1 EP 1739378 A1 EP1739378 A1 EP 1739378A1 EP 06011707 A EP06011707 A EP 06011707A EP 06011707 A EP06011707 A EP 06011707A EP 1739378 A1 EP1739378 A1 EP 1739378A1
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EP
European Patent Office
Prior art keywords
heat exchange
exchange element
element according
shafts
heat
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Withdrawn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
EP06011707A
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German (de)
English (en)
Inventor
Jörg Dr. Leuschner
Michael Kozica
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.)
Autokuehler GmbH and Co KG
Original Assignee
Autokuehler GmbH and Co KG
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 Autokuehler GmbH and Co KG filed Critical Autokuehler GmbH and Co KG
Publication of EP1739378A1 publication Critical patent/EP1739378A1/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Withdrawn legal-status Critical Current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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • 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
    • F28D2021/0028—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cooling heat generating elements, e.g. for cooling electronic components or electric devices
    • F28D2021/0029—Heat sinks

Definitions

  • the invention relates to a heat exchange element of the type specified in the preamble of claim 1 and a heat exchanger produced therewith.
  • Heat exchange elements with adjacent, smooth walls, which form between them flow channels, depending on the application components of tube, plate or rib heat exchangers and / or as baffles or fins (corrugated fins) are formed. They are z. As used in motor vehicles, compressors, dryers, air conditioning and refrigeration systems or refrigeration dryers for compressed air systems and for cooling of electronic components and in numerous machines such. B. construction, agricultural and forestry machines used.
  • the flow channels of such heat exchange elements are usually limited by smooth, flat walls, depending on the application of a fluid such. As air, water or oil are flowed through and serve to transfer heat to the respective fluid or to receive from this.
  • Laminar or turbulent flows develop in the flow channels, leading to characteristic boundary layers in the zones adjacent to the walls, in which the fluids flowing through are ideally at a standstill in the ideal case of a laminar flow.
  • the fluids are in each case moved at the greatest speed through the flow channel.
  • boundary layers has the consequence that the existing wall surfaces are only partially usable for the heat transfer and the achievable heat exchange rates are low. It has therefore been known for a long time ( DE-PS 596 871 ), to provide the walls of the flow channels with emerging from the wall surface, vortex generating features that are parallel or at acute angles to the flow axis. As a result, the parts of the fluid streams close to the walls are repeatedly divided to form local vortices and the otherwise forming boundary layers are torn open and destroyed. As a result, there is a marked improvement in heat exchange performance.
  • the described vortex-forming characteristics can lead to two disadvantages. On the one hand, they can not only divert the parts of the flow close to the walls in the direction of the core zones and thereby increase the heat exchange performance, but also reduce the flow cross sections and thereby lead to an undesirable increase in the pressure losses occurring along the flow channels. As a result, the flow passages passing through the volume flows are reduced according to natural convection, while forced convection powerful fans, pumps od. Like. Needed to maintain a preselected flow rate. On the other hand, characteristics of the type described due to their cross-sectional shapes tend to contamination, especially if they are z. B. are used in cooling for agricultural, forestry and construction machinery or vehicles or in household clothes dryers and the fluid is the process air and / or the cooling air.
  • heat exchange elements of the type described at the outset have already become known (eg. U.S. Patent 3,907,032 ), in which the walls delimiting the flow channels are provided with shafts extending transversely to the flow direction or are of a continuous wave-shaped design. Even with such heat exchange elements can be achieved so far no optimal results, either an unfavorable power / pressure drop ratio or in the attempt to optimize this, an increased tendency to fouling is obtained. This is true even if the waves are given certain dimensions or comparatively complicated shapes (eg. DE 195 03 766 A1 . EP 1 357 345 A2 ). Also known heat exchange elements in which adjacent walls are provided with differently structured corrugations (eg. DE 102 18 274 A1 ), on the other hand, have the disadvantage, in particular, that their flow channels have comparatively strongly fluctuating cross sections, which is not conducive to a reduction of the pressure losses.
  • the object of the present invention is to form the heat exchange element of the type described above so that an increase the ratio heat exchange performance to pressure loss is achieved while reducing the tendency to fouling, especially when it comes to the heat exchange with gaseous fluids.
  • the invention will be particularly useful in conjunction with gaseous fluids such.
  • gaseous fluids such as dirt, dirt, and water.
  • the waves are designed so that the tendency to fouling is low.
  • the heat exchange elements according to the invention and thus equipped heat exchangers are therefore particularly well suited for applications in coolers for agricultural, forestry and construction machinery and in dryers, intercoolers of vehicles or devices for cooling electronic components.
  • Fig. 1 to 3 show a heat exchange element according to the invention on the basis of a currently considered best embodiment.
  • the heat exchange element comprises a plurality of juxtaposed, heat transferring, and preferably mutually parallel walls 1.
  • the walls 1 are formed by thin plates having a height D (FIG. 1) and a thickness S (FIG. 2), and at their ends shown in FIG 1 upper and lower longitudinal edges by upper and lower, also plate-shaped connecting portions 2a, 2b meandered together.
  • the flow channels 4 are open.
  • the open in Fig. 1 transversely to the longitudinal direction up or down areas the flow channels 4 are, however, in the application of the heat exchange element of FIG. 1 od usually by a not-shown functional part of a heat exchanger. The like. Closed.
  • the flow channels 4 serve the purpose of being flowed through in the direction of the arrows 3 or in the opposite direction by a fluid (eg, air, water, oil or the like), which thereby flows with the walls 1 and the connection sections 2a, 2b comes into heat-exchanging contact and is therefore cooled or heated as the case may be.
  • a fluid eg, air, water, oil or the like
  • the walls 1 are made of materials common in heat exchangers (eg a metal such as aluminum or copper, graphite, a plastic or the like). They are also preferably smooth, d. H. at their the flow channels 4 facing, arranged between the upper and lower edges broadsides 5a, 5b neither with nubs, scales or other forms nor with openings in the form of cuts, openings od. Like. Provided. This disturbing dirt angle od. Like. In the flow channels 4 largely or completely avoided.
  • Fig. 2 shows four adjacent walls 1 in the plan view, wherein the non-essential connecting portions 2a, 2b (Fig. 1) are omitted to avoid confusion.
  • all walls 1 are formed substantially identical and with their broad sides 5a and 5b facing each other in pairs to form the flow channels 4.
  • the walls 1 are provided in known manner with corrugations or sinusoidal waves 6, said corrugations 6 forming the walls 1 by deformation Plates are obtained around lines that extend in the direction of their height D and substantially parallel to the broad sides 5a, 5b of the walls 1 according to FIG.
  • Fig. 3 shows that the waves 6 extend alternately on one or the other side of an imaginary, indicated by a dashed line center plane 7, the center plane of the original, undeformed, plane-parallel Plate corresponds.
  • the shafts 6 each contain a first, in the flow direction 3 leading half-wave 6a (Fig.
  • the shafts 6 are formed in all walls 1 of the heat exchange element of FIG. 1 in the same way and parallel and in the flow direction 3 without offset, d. H. arranged at a constant clearance relative to one another, so that the flow channels 4 according to FIG. 2 have substantially the same channel width corresponding to a dimension B substantially.
  • the shafts 6 have upper and lower peaks 9 a and 9 b curved around lines lying in the central planes 7. 2 and 3 have a dimension W, measured between the high and low points of imaginary center lines of the walls 1.
  • the waves 6 in the region of the vertices 9a, 9b each have radii of curvature corresponding to one Dimension R in FIGS. 2 and 3.
  • the heat exchange element is designed so that on the one hand by increasing the heat exchanging surfaces per unit volume achieved an increase in performance, on the other hand by large curve radii within the flow channels 4, both the pressure loss and the tendency to fouling is limited.
  • the channel width B of the invention Heat exchanger element corresponding to the inequality B ⁇ 0.55 W significantly smaller than the vertex distance W to choose.
  • a ratio B / W has proven to be advantageous which satisfies the inequality 0.1 ⁇ B / W ⁇ 0.55, with the inequality 0.35 ⁇ B / W ⁇ 0.50 being particularly preferred. It is thereby achieved that the fluid flow, as indicated by arrows in FIG. 2, is deflected in the region of each half-wave 6a, 6b, instead of being conducted through the flow channels 4 without substantial deflection and practically straight ahead, as is the case for conventional heat exchange elements. in which the channel width B is greater than the vertex distance W or at most slightly smaller than this.
  • the measure B ⁇ 0.55 W has the consequence that the waves 6 according to FIG. 2 overlap to a large extent transversely to the center planes 7, ie each half-wave 6a, 6b deep into the above or below located half-wave 6a, 6b protrudes the adjacent wall 1, and that by a little more than the position of the respective center plane 7 corresponds.
  • the resulting denser packing or smaller pitch T (FIG. 1) of the walls 1 leads to a considerable increase in performance of the heat exchange element per unit volume.
  • the advantage is achieved that the deflections of the fluid in the flow channels 4, although significant, but compared to designs in which the Krümungsradien be a maximum of 3 mm or even much smaller, takes place relatively gently, which has much smaller pressure losses result.
  • the inventive design of the shafts 6 and the channel widths B also allows the use of larger angles ⁇ and ⁇ (Fig. 3) for those of the center planes As a result, the advantage is achieved that at the same channel widths B and wavelengths ⁇ larger overlaps of the shafts 6 and half-waves 6a, 6b are possible and thus the heat-exchanging surfaces can be increased.
  • the angles ⁇ and ⁇ should preferably be no greater than 40 °.
  • FIG. 3 shows, in particular, that the rising and falling portions of the half-waves 6a, 6b are preferably straight and are connected in the region of the vertices 9a, 9b by curved sections with the radii R. This results in a triangular appearance for the walls 1, wherein only the vertices 9a, 9b convex, d. H. are rounded off to the middle planes 7 out.
  • Fig. 4 shows a substantially corresponding to the embodiment of FIG. 3 corresponding wall 11. A difference is only that the curved sections lying in the apex have different radii of curvature R1 to R4. In this case, preferably all radii R1 to R4 are within the ranges indicated above.
  • Fig. 5 shows a wall 12 of a heat exchanger element according to the invention, which has exclusively straight and planar sections.
  • a first half-wave 14a of a shaft 14 has a flat portion 15 rising straight at the angle ⁇ , a flat portion 16 just dropping with the angle ⁇ , and a flat portion 17 connecting both in the region of the vertex, which preferably is arranged parallel to the median plane 7.
  • the radius of curvature R ⁇ .
  • section 17 has a length (eg L 1 ) which is so large that the two respective ends of the sections 15, 16 could optionally also be connected by an imaginary curved section 18 indicated by dashed lines, whose radius of curvature is in the above ranges.
  • the lengths of the straight portions 17 can all be the same length or, as indicated in Fig. 5 by dimensions L 1 to L 4 , be different lengths.
  • FIG. 6 shows an exemplary embodiment of a wall 20 according to the invention which, as described above, has half shafts 21a, 21b which are connected to each other by straight, flat and preferably in the middle planes 7 sections 22, which are the same length or different lengths can.
  • Fig. 6 shows that the half-waves 21a, 21b with respect to the center planes 7 may have different peak heights W 1 and W 2 , which add to the vertex distance W.
  • different peak heights W 1 , W 2 can also be provided in the exemplary embodiments according to FIGS. 1 to 5 without thereby deviating from the stated dimensions for the vertex distance W.
  • FIG. 7 shows four heat exchange elements 23 to 26 according to the invention, which are distinguished by different total lengths measured in the flow direction 3, which are obtained by a different number of three, four, five or six waves lying one behind the other in the flow direction 3. It can be seen that the waves can have different shapes and / or dimensions.
  • Fig. 7 shows that the flow channels 4 preferably inlet and / or outlet ends 27, 28, which are parallel to the center planes not shown here, so that the fluid does not enter the heat exchange element 23 to 27 or when flowing out of this is redirected in a pressure loss favorable way.
  • the wavelengths ⁇ and / or the vertexes W in the flow direction 3 gradually larger or - as in the embodiment of Fig. 8 by wavelengths ⁇ 1 , ⁇ 2 and ⁇ 3 and the vertexes W 3 , W 4 and W 5 is shown - gradually let smaller. This makes it possible to achieve a gradually more intense vortex formation in the direction of the flow and thus a gradually increasing heat transfer performance.
  • FIG. 8 shows that the half-waves on both sides of their vertices can also be formed asymmetrically.
  • Fig. 9 shows a flat-tube heat exchanger with flat tubes 31, between which according to Fig. 1 to 8 formed heat exchange elements in the form of fins 32 (corrugated fins) are arranged.
  • the slats 32 are folded in a meandering manner analogous to FIG. 1 and provided with side walls 33 which are interconnected by substantially flat, upper and lower connecting portions 34a, 34b.
  • the side walls 33 are provided according to the invention with shafts, which are formed analogously to FIGS. 3 to 8.
  • the side walls 33 each bound flow channels through which z. B. a gaseous cooling medium flows to cool a liquid flowing in the flat tubes 31, liquid.
  • the flow directions are indicated by arrows 35, 36 by way of example.
  • Fig. 10 shows a heat exchanger in conventional plate construction.
  • the heat exchanger includes a plurality of parallel and stacked rectangular plates 38 alternately extending at their edges by profiles 39 extending parallel to the long sides and parallel to the short sides extended profiles 40 are kept at a distance. This results in between the plates 38 and profiles 39 and 40 extending in the longitudinal direction flow channels 41 for a first fluid and transverse thereto flow channels 42 for a second fluid.
  • flow channels 41 and / or 42 also schematically indicated, here zigzag or wavy instead of meandering formed fins 43, 44 are arranged, which serve to improve the heat transfer between the two fluids.
  • the reference numeral 45 also indicates one of the two common collection boxes, by means of which the first fluid, for. B.
  • the plates 38, profiles 39 and 40, fins 43 and 44 and the collecting boxes 45 can be in a conventional manner z. B. be joined together by gluing or soldering.
  • the fins 43 and / or 44 have side walls 46, which are formed according to FIGS. 1 to 8.
  • the flow directions for the fluids are indicated by arrows by way of example.
  • Figure 11 shows a heat exchange element having a plurality of heat transferring walls 48 disposed in parallel juxtaposition and formed by thin, undulating plates.
  • the walls 48 are fixed to lower narrow sides by soldering, gluing or otherwise on a wall 48 firmly interconnecting base plate 49 and have, starting from the base plate 49, a height D.
  • the two mutually opposite broad sides 50 of the walls 48 limit one Flow channel 51 for a fluid.
  • the base plate 49 is z. B. to be cooled electronic component, so that the heat exchange element forms a rib heat sink.
  • the flow channels 51 in the direction of their parallel to the base plate 49 extending longitudinal axis z. B. flows through cooling air, wherein a selected flow direction is exemplified by an arrow 52.
  • the general statements apply to Fig. 1 to 10 accordingly.
  • the described embodiments bring, in addition to a noticeable increase in performance at most a small percentage increase in pressure losses with it. This is a consequence of the fact that, on the one hand, a substantially larger, heat-exchanging surface is present and the flow path for the fluid is correspondingly longer, while on the other hand the flow can easily follow the rounded flow channels.
  • there is the particular advantage that the tendency to fouling in the flow channels despite the waves is low because the broad channels limiting the flow channels are consistently flat or slightly rounded and smooth and form no disturbing corners and angles. This is true even if the extent of the overlap of the shafts 6 described with reference to FIG.
  • the invention is not limited to the described embodiments, which can be modified in many ways. This is especially true for the specified shapes and / or sizes of the different waves and for the density of their arrangement.
  • the choice of the various parameters is largely dependent on the individual case and the desired heat exchange or heat transfer performance.
  • the curved portions provided in the crests of the shafts may be circular as well as elliptical or follow other curves.
  • z. B. designed as baffles heat exchange elements and equipped with these heat exchanger can be applied.
  • the given dimensions and / or inequalities in the heat exchange elements and heat exchangers produced therewith should be at least partially, but particularly preferably continuously present, although variations of these dimensions and / or inequalities within one and the same heat exchange element or heat exchanger are possible.
  • the various features may be combined with each other in a manner other than described and illustrated in the drawings.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP06011707A 2005-06-23 2006-06-07 Element d'échange de chaleur et échangeur de chaleur associé Withdrawn EP1739378A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202005009948U DE202005009948U1 (de) 2005-06-23 2005-06-23 Wärmeaustauschelement und damit hergestellter Wärmeaustauscher

Publications (1)

Publication Number Publication Date
EP1739378A1 true EP1739378A1 (fr) 2007-01-03

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EP06011707A Withdrawn EP1739378A1 (fr) 2005-06-23 2006-06-07 Element d'échange de chaleur et échangeur de chaleur associé

Country Status (5)

Country Link
US (1) US20060289152A1 (fr)
EP (1) EP1739378A1 (fr)
KR (1) KR20060134864A (fr)
CN (1) CN100595509C (fr)
DE (1) DE202005009948U1 (fr)

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DE202007017501U1 (de) 2007-12-13 2009-04-23 Autokühler GmbH & Co. KG Wärmeaustauschelement und damit hergestellter Wärmeaustauscher
WO2009078289A3 (fr) * 2007-12-14 2009-09-17 Toyota Jidosha Kabushiki Kaisha Ailette de refroidissement et procédé de fabrication correspondant
EP2315244A1 (fr) * 2009-10-26 2011-04-27 Kabushiki Kaisha Toyota Jidoshokki Dispositif refroidissant de type refroidissement par liquide
EP2339620A3 (fr) * 2008-07-04 2013-10-09 Kabushiki Kaisha Toyota Jidoshokki Dispositif semi-conducteur
EP3106817A1 (fr) * 2015-06-18 2016-12-21 Hamilton Sundstrand Corporation Échangeur thermique à ailettes-plaques
WO2018106102A1 (fr) * 2016-12-07 2018-06-14 Recair Holding B.V. Récupérateur
EP3517440A1 (fr) * 2018-01-24 2019-07-31 Hamilton Sundstrand Corporation Échangeur tri-thermique de système de commande environnemental
US10473403B2 (en) 2010-11-19 2019-11-12 Danfoss A/S Heat exchanger
FR3126760A1 (fr) * 2021-09-03 2023-03-10 Valeo Systemes Thermiques Echangeur de chaleur d’une boucle de fluide refrigerant.

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CN1884958A (zh) 2006-12-27
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DE202005009948U1 (de) 2006-11-16
CN100595509C (zh) 2010-03-24

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