EP1770345A2 - Réseau d'échange de chaleur et échangeur de chaleur comprenant celui-ci - Google Patents

Réseau d'échange de chaleur et échangeur de chaleur comprenant celui-ci Download PDF

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Publication number
EP1770345A2
EP1770345A2 EP06018503A EP06018503A EP1770345A2 EP 1770345 A2 EP1770345 A2 EP 1770345A2 EP 06018503 A EP06018503 A EP 06018503A EP 06018503 A EP06018503 A EP 06018503A EP 1770345 A2 EP1770345 A2 EP 1770345A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
network according
exchanger network
air
refrigerant
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
EP06018503A
Other languages
German (de)
English (en)
Other versions
EP1770345A3 (fr
EP1770345B1 (fr
Inventor
Josef Gievers
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 EP1770345A2 publication Critical patent/EP1770345A2/fr
Publication of EP1770345A3 publication Critical patent/EP1770345A3/fr
Application granted granted Critical
Publication of EP1770345B1 publication Critical patent/EP1770345B1/fr
Not-in-force 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
    • 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
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • F28D9/0068—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 with means for changing flow direction of one heat exchange medium, e.g. using deflecting zones
    • 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
    • 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
    • F28D2021/0038—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for drying or dehumidifying gases or vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/108—Particular pattern of flow of the heat exchange media with combined cross flow and parallel flow

Definitions

  • the invention relates to a heat exchanger network of the type specified in the preamble of claim 1 and a heat exchanger equipped therewith.
  • heat exchanger networks of this type produced heat exchangers are z. B. needed in compressed air systems to that produced by a compressor and under a pressure of z. B. 25 bar standing compressed air to remove the moisture to make them critical applications such. B. in the food and paper industry or in the medical field to make suitable.
  • the air drying takes place in that the heated air coming from the compressor is passed after passage through an aftercooler through a device containing an air / air and a refrigerant / air heat exchanger.
  • the air / air heat exchanger is usually made in the manner of a plate heat exchanger of conventional construction
  • the refrigerant / air heat exchanger z.
  • Example from a combined pipe / plate heat exchanger with a network, which has formed from plates and these spaced-apart strips air passages and intermediate refrigerant passages. These consist z. B. arranged between each two plates, round or square cross-sections having tubes, the straight sections and these serpentine or meandering have connecting deflecting sections ( EP 0 521 298 A2 ).
  • a disadvantage of this construction is that between the individual pipe sections unused spaces arise and the curved deflection sections are usually outside of the space occupied by the actual network and are not involved in the heat exchange.
  • the dividing walls are formed by the webs and / or flanges of profiles arranged between the plates with I- and / or U-shaped cross sections ( EP 1 304 536 A2 ). If the flow channels are produced according to a first variant by means of a plurality of I-profiles, which are connected to the plates by soldering, then these profiles od before the soldering at least two points by laser welding. Like, are connected to the plates, to exclude relative position changes between the plates and the profiles during the dipping and tilting processes required during the soldering process.
  • the flow channels are formed according to a second variant as U-shaped grooves in solid, plane-parallel plates, these and the deflection zones must be produced by milling, in particular track milling. Both variants cause comparatively high production costs, which are not always sustainable.
  • the invention the technical problem underlying the heat exchanger network of the type described above in such a way that it can be produced using cost-effective manufacturing process with the required strength, is problematic in soldering technology and yet allows for given overall dimensions comparatively large flow cross sections for the refrigerant.
  • lamellae which each form a plurality of flow channels
  • the number of welding operations to be carried out before the soldering operation can be considerably reduced.
  • the slats can be produced by extrusion or milling and thereby cost-effectively with any strength.
  • the dividing walls and / or the limited of these flow channels in principle any cross-sectional shape can be given, which is favorable in view of the desired performance and stability of the heat exchange network in each case.
  • a heat exchanger apparatus for refrigeration dryers in compressed air systems includes according to Fig. 1 to 3 in the right section of a refrigerant / air heat exchanger and the left section of an air / air heat exchanger.
  • the two nets 1 and 2 are mainly formed by plane-parallel, rectangular or square plates or dividers 4, which are extended over the entire width and length of the trestle 3.
  • 1 and 3 is a part of the plates 4 on the one hand by perpendicular to the longitudinal direction strips 5, which are arranged on the left in Fig. 3 ends of the block 3, and on the other hand by extending in the longitudinal direction, arranged on the side edges of the plates 4 Bars 6, 7 kept in pairs at a distance.
  • the upper strips 6 are slightly shorter, so that between their left ends and the strips 5 each interspaces 9 arise by the air in the direction of an arrow 10 indicated laterally enter can.
  • the other part of the plates 4 is shown in FIG. 1 and 2 in the network 2 forming portion by parallel to the longitudinal direction, arranged on the side edges of the plates 4 strips 15 and 16 and extending transversely thereto, the left and right end of the network. 2 forming end strips 17 and 18 kept in pairs at a distance.
  • end strips 18 in Fig. 2 upper strips 15 are slightly shorter, so that between them and the end strips 18 each gaps 20 arise through the air can be supplied laterally in the direction of an arrow 21 (FIG. 2).
  • the strips 16 a little shorter, so that between them and the end strips 17 gaps 22 arise through which the air supplied at 20 can be removed again (arrow 23).
  • the deflections are carried out analogously to FIG. 3, preferably with correspondingly formed slats provided in the passages 19 (FIG. 1).
  • the same plates 4 delimiting the passages 19 serve to form serpentinely arranged passageways 24 (Fig. 1) which have straight and diverting portions, as explained in more detail below.
  • the passages 24 each extend from the end strips 18 to a terminal strip or plate 25, which is arranged in Fig. 1 and 2 at the right end of the block 3.
  • plates 4 alternate with the passages 8 and plates 4 with the passages 19, 24 in superimposed planes, wherein at least one passage 8, 19, 24 is present in each plane.
  • the passages 24 are supplied at a inlet indicated by an arrow 26 with a refrigerant which can flow out again at an exit indicated by an arrow 27 and flows through a refrigerant circuit (not shown).
  • Heat exchangers of the type described and their mode of action are generally known to the person skilled in the art (EP 0 521 298 A2 . EP 1 304 536 A2 ) and therefore need not be explained in detail.
  • FIGS. 4 to 9 The embodiment according to the invention of a refrigerant passage 24 of the network 1 is explained in more detail below with reference to FIGS. 4 to 9, wherein for the sake of simplicity of the description the terms “right”, “left”, “from”, “rear”, “top” and “bottom “are selected according to the respective situation, which results from the special representation in Fig. 4 to 9.
  • the passage 24 is formed by a plurality of parallel juxtaposed slats 31 ( Figures 4 to 7).
  • Each blade 31 has, according to FIGS. 6 and 7, a meander-shaped cross-section and a plurality of, in the exemplary embodiment, five partition walls 32. As also shown in Figs.
  • the dividing walls 32 are arranged vertically, parallel to each other and equidistant from each other and alternately connected at the top and bottom by horizontal, upper and lower webs 33, 34, respectively, as is typical of meanders . Because of the presence of five partitions 32, two upper and two lower webs 33, 34 are provided, so that each two adjacent partitions 32 and a connecting web 33 or 34 define a flow channel 35 and a total of four such flow channels 35 per blade 31 are present. In this case, the arrangement is preferably made such that each flow channel 35 has the same flow cross-section. At the lateral ends of the blade 31 is bounded by one of the partitions 32.
  • the lamellae 31 are preferably produced by extrusion of aluminum or an aluminum alloy and subsequent cutting to the desired length in the individual case. Therefore, their partitions 32 are initially of equal length and each with a front and rear end and a front or rear end face 32a, 32b (Fig. 5). After cutting to length, however, the dividing walls 32 are provided with a recess 36 at one or the other end 32a, 32b. As indicated in Fig. 5 by dashed lines, for this purpose z. B. od the last, at the end 32a, 32b adjacent portion of the partition 32 by milling od. Like. Removes, whereupon for grinding the ridges od a cleaning operation with a steel brush. Like. Can connect. As particularly shown in FIG. 4, the recesses 36 are alternately attached at successive partitions 32 at the one or the other end 32a, 32b, so that in the embodiment at the front end of the blade 31 three and at the rear end of the blade 31, two such recesses 36th to come to rest.
  • FIGS. 8 and 8 show a refrigerant passage 24 produced by use of the fins 31 and arranged in a plane.
  • the complete section of the heat exchanger device containing the network 1 is shown enlarged.
  • a first lamella 31a is arranged parallel to and at a distance corresponding to the width of a flow channel 35 from the end strip 18.
  • the position of the lamella 31a is selected so that an outer, leftmost partition wall 32a arranged parallel to the bar 18 and its recess 36 is provided on the not shown in Fig. 9, the rear end of the blade 31a. This is z. B. the blade 31 shown in Fig.
  • FIG. 8 corresponding to the meandering shape, three middle dividing walls 32b, 32c and 32d and a further outer dividing wall 32e are connected to the dividing wall 32a, which is indicated by dashed lines like the other dividing walls 32 in FIG. 9, which in FIG 8 and 9 are furthest to the right. Due to the arrangement of the recesses 36 described with reference to FIGS. 4 to 7, the two recesses are formed 36 of the partitions 32b, 32d and three not visible in Fig. 9 recesses 36 of the partition walls 32a, 32c and 32e to lie behind. This is best seen in FIG. 11.
  • the blade 31a is followed by a second blade 31b in FIGS. 8 and 9.
  • This is identical to the blade 31a formed, but compared to this in the apparent from Fig. 4 and 6 position, so that in her three recesses 36 from and two further, not visible in Fig. 9 recesses 36 are behind.
  • a leftmost partition wall 32f of the sipe 31b having a width corresponding to the width of a flow channel 35 is disposed away from and parallel to the partition wall 32e of the sipe 31a. This, too, is best seen in FIG. 11.
  • the alternately upwardly and downwardly open flow channels 35 are closed in accordance with FIG. 8 upwards or downwards by one of the plates 4, which are expediently connected to the outer sides of the webs 33, 34 by soldering.
  • the front and rear ends of the flow channels 35 are closed by individual profiles 37 having a width substantially equal to twice the distance of two partitions 32, with the front and rear ends of the fins 31 a and 31 b and the partitions 32 and with the Plates 4 are preferably connected gas-tight by welding (MIG or TIG) and for weight and cost reduction z.
  • MIG or TIG gas-tight by welding
  • B. have the apparent from Fig. 9, trapezoidal cross-sections.
  • flow channels 38, 38 a, 38 b are sealed gas-tight between the blade 31 a and the end strip 18, between the blades 31 a and 31 b (eg., Fig. 8) and the other side of the network 1 between the last lamella 31 and the end strip 25 (FIGS. 10 and 11) are formed, the two flow channels 38 and 38b corresponding to FIG. B. remain open at the front, there to the refrigerant in the direction of arrows 26, 27 and to be able to discharge.
  • the described recesses 36 form, after the completion of the refrigerant passages 24 (FIGS. 11 and 13), a deflection zone alternately from or at the rear, bounded by the respective plates 4, profiles 37 (or plate 39) and partitions 32.
  • the refrigerant therefore flows along a serpentine, in Fig. 11 and 13 partially marked by arrows flow path through the passage 24th
  • corresponding passages 24 may be present and separated by air passages from each other, as in particular Figs. 1 to 3 and 10, 12 make clear.
  • the profiles 37 and plates 39 suitably extend over the entire height of the heat exchange network.
  • the number of flow channels 35 and 38, from which the refrigerant passages 24 may be selected depending on the requirements of the case. Instead of the four flow channels 35 according to FIGS. 6 and 7, more or fewer flow channels 35 per blade 31 may also be present. In an even number of partitions 32 per blade 31, these can be laid in particular with the same orientation, since in this case the recesses 36 of the first partition wall 32 is always z. B. from and the recesses 36 of the last partition wall 32 always z. B. come to lie behind. Combinations with different numbers of dividing walls 32 and flow channels 35 are also possible, whereby adjacent fins 31 can also be arranged directly next to each other, in which case the flow channels 38 located between them would be missing.
  • slats 31 with a smaller number of partitions 32 have the advantage that they are only slightly curved during extrusion because of the more uniform flow of material and therefore can be straightened during the successful before soldering setting the heat exchanger network 1.
  • the assembly of the heat exchanger block 3 of FIG. 1 is carried out in a conventional manner in heat exchangers by z. B. first, the plates 4 and fins 31 connected by soldering and then the profiles 37 (or plates 39) are fixed by welding to the plates 4 and fins 31. This results in the advantage that the blades 31 must be connected before soldering to secure the position only at two points, each with an associated plate 4 by welding, while using individual profiles as partitions (in the embodiment, five individual profiles per blade) each 10th Welding operations were required.
  • FIGS. 16 and 17 show a second embodiment of the blade 31 according to the invention, which, in contrast to the blade 31 of FIGS. 6 and 7 not only an even number of partitions 32, but also on one side with a foot or web 34a instead of a partition wall 32 ends.
  • This web 34a protrudes from one associated, end-side partition wall 32 to the outside, as Figs. 16 and 17 clearly show.
  • the web 34a specifies the distance of two adjacent blades 31.
  • the advantage is achieved that care must be taken when setting the network 2, whether the lamellae 31 have the correct distances from each other, as in Fig. 8 applies to the adjacent to the flow channel 38a lamellae 31.
  • the web 34a z For example, in Fig. 11, they may be applied with an impact to the endmost ledge 25 located on the far right to form the flow channel 38b (Fig. 11).
  • a blade 31 as shown in FIG. 18 to 21 is provided on both sides with each a foot or web 34b, 34c which projects from an associated, end-side partition 32 to the outside, as shown in particular Fig. 20 and 21 show.
  • a web (eg 34b) is expediently arranged at the top and the other web (eg 34c) at the bottom.
  • Adjoining this lamella is then a lamella, designated by the reference numeral 31d in FIG. 22, according to FIG. 16, so that a dividing wall 32g located at the far left abuts the web 34c from the latter. 16 may then be joined to this lamella 31 until the terminal strip 25 (FIG. 11) is reached, against which the web 34a abuts, whereby the flow channel 38b (FIG. 11) is formed. In this way, the entire network 2 can be set without a distance between two slats 31 erroneously too large or too small fails.
  • the invention is not limited to the described embodiments, which could be modified in many ways.
  • the webs 33 and 34 and / or the spacers 40 could be slightly convex curved to obtain a desired to improve the soldering crown.
  • the lamellae 31 and profiles 37 (or plates 39) As aluminum and the plates 4 made of clad aluminum, but it is clear that, depending on requirements, other commonly used for the production of politicians can be used.
  • the networks 1 and 2 form an integral component by means of the continuous plates 4, manufactured separately and then assembled into an integral component or find application as separate components that are used independently or by appropriate lines with each other get connected.
  • the nets 1, 2 can also be arranged one above the other instead of side by side.
  • the various features may be provided in combinations other than those described and illustrated.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP06018503A 2005-09-28 2006-09-04 Réseau d'échange de chaleur et échangeur de chaleur comprenant celui-ci Not-in-force EP1770345B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE202005015627U DE202005015627U1 (de) 2005-09-28 2005-09-28 Wärmeaustauschernetz und damit ausgerüsteter Wärmeaustauscher

Publications (3)

Publication Number Publication Date
EP1770345A2 true EP1770345A2 (fr) 2007-04-04
EP1770345A3 EP1770345A3 (fr) 2008-12-17
EP1770345B1 EP1770345B1 (fr) 2012-08-01

Family

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EP06018503A Not-in-force EP1770345B1 (fr) 2005-09-28 2006-09-04 Réseau d'échange de chaleur et échangeur de chaleur comprenant celui-ci

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Country Link
US (1) US20070137843A1 (fr)
EP (1) EP1770345B1 (fr)
JP (1) JP2007093199A (fr)
DE (1) DE202005015627U1 (fr)

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CN101925371B (zh) * 2008-01-23 2013-01-16 株式会社Jms 医疗用换热器及其制造方法以及人工肺装置
BE1018518A3 (nl) * 2009-04-06 2011-02-01 Atlas Copco Airpower Nv Verbeterde warmtewisselaar.
DE102009050482B4 (de) * 2009-10-23 2011-09-01 Voith Patent Gmbh Wärmeübertragerplatte und Verdampfer mit einer solchen
EP2377596B9 (fr) 2010-04-14 2016-04-13 Kaeser Kompressoren Se Dispositif de séchage à froid, notamment dispositif de séchage à froid à air comprimé, ainsi qu'échangeur de chaleur pour un dispositif de séchage à froid, notamment dispositif de séchage à froid à air comprimé
EP2879162B1 (fr) * 2012-07-27 2020-07-29 Kyocera Corporation Organe de chemin d'écoulement et échangeur de chaleur et dispositif de fabrication de semi-conducteurs l'utilisant
CA2839884C (fr) * 2013-02-19 2020-10-27 Scambia Holdings Cyprus Limited Echangeur thermique a plaques comprenant des elements de separation
US10823511B2 (en) * 2017-06-26 2020-11-03 Raytheon Technologies Corporation Manufacturing a heat exchanger using a material buildup process
DE102022209786A1 (de) * 2022-09-16 2024-03-21 Robert Bosch Gesellschaft mit beschränkter Haftung Wärmetauscher zur Kühlung von Komponenten

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EP0393937A2 (fr) * 1989-04-19 1990-10-24 John Francis Urch Echangeur
BE1008176A6 (nl) * 1994-03-07 1996-02-06 Atlas Copco Airpower Nv Werkwijze voor het drogen van een gekomprimeerd gas en inrichting om deze werkwijze te verwezenlijken.
EP1304536A2 (fr) * 2001-10-17 2003-04-23 Autokühler Gmbh & Co. Kg. Système d'échange de chaleur réfrigérant / air
WO2003071213A1 (fr) * 2002-02-19 2003-08-28 Dana Canada Corporation Echangeur de chaleur a ailettes de forme compacte
DE20315267U1 (de) * 2002-10-21 2004-03-04 Autokühler GmbH & Co. KG Vorrichtung zur Abkühlung und Trocknung von Luft, insbesondere für Kältemitteltrockner von Druckluftanlagen
JP2004150760A (ja) * 2002-10-31 2004-05-27 Denso Corp 熱交換器

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Publication number Priority date Publication date Assignee Title
EP0393937A2 (fr) * 1989-04-19 1990-10-24 John Francis Urch Echangeur
BE1008176A6 (nl) * 1994-03-07 1996-02-06 Atlas Copco Airpower Nv Werkwijze voor het drogen van een gekomprimeerd gas en inrichting om deze werkwijze te verwezenlijken.
EP1304536A2 (fr) * 2001-10-17 2003-04-23 Autokühler Gmbh & Co. Kg. Système d'échange de chaleur réfrigérant / air
WO2003071213A1 (fr) * 2002-02-19 2003-08-28 Dana Canada Corporation Echangeur de chaleur a ailettes de forme compacte
DE20315267U1 (de) * 2002-10-21 2004-03-04 Autokühler GmbH & Co. KG Vorrichtung zur Abkühlung und Trocknung von Luft, insbesondere für Kältemitteltrockner von Druckluftanlagen
JP2004150760A (ja) * 2002-10-31 2004-05-27 Denso Corp 熱交換器

Also Published As

Publication number Publication date
EP1770345A3 (fr) 2008-12-17
EP1770345B1 (fr) 2012-08-01
JP2007093199A (ja) 2007-04-12
US20070137843A1 (en) 2007-06-21
DE202005015627U1 (de) 2007-02-08

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