EP2238401A1 - Échangeur de chaleur à structure de conduites fractale - Google Patents

Échangeur de chaleur à structure de conduites fractale

Info

Publication number
EP2238401A1
EP2238401A1 EP09706056A EP09706056A EP2238401A1 EP 2238401 A1 EP2238401 A1 EP 2238401A1 EP 09706056 A EP09706056 A EP 09706056A EP 09706056 A EP09706056 A EP 09706056A EP 2238401 A1 EP2238401 A1 EP 2238401A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger according
line
points
inflow port
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Withdrawn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
EP09706056A
Other languages
German (de)
English (en)
Inventor
Tetyana Lapchenko
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.)
BSH Hausgeraete GmbH
Original Assignee
BSH Bosch und Siemens Hausgeraete GmbH
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 BSH Bosch und Siemens Hausgeraete GmbH filed Critical BSH Bosch und Siemens Hausgeraete GmbH
Publication of EP2238401A1 publication Critical patent/EP2238401A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • F25B39/024—Evaporators with plate-like or laminated elements with elements constructed in the shape of a hollow panel
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • 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
    • F28F2210/02—Heat exchange conduits with particular branching, e.g. fractal conduit arrangements

Definitions

  • the present invention relates to a heat exchanger and in particular a heat exchanger which is suitable for use as an evaporator in a refrigeration appliance.
  • Known heat exchangers with unbranched line structure usually comprise a substrate, on which a continuous line extends in meanders from an inflow to an outflow connection.
  • a temperature change associated with the supply of heat transfer fluid spreads over the entire surface of the substrate in a short time.
  • the disadvantage is that the large length of the single line causes a high pressure drop of the heat transfer fluid in the heat exchanger, so that a high drive power for circulating the heat transfer fluid is required.
  • the meandering path allows heat exchange between adjacent upstream and downstream portions of the conduit, which reduces the effectiveness of the heat exchanger.
  • a heat exchanger with a branched line structure as known, for example, from EP 1 525 428 B1, has the advantage that the multiplicity of parallel paths of the heat transfer fluid extending between the inflow and outflow connection reduces the pressure drop in the heat exchanger.
  • a disadvantage of these heat exchangers is the nonuniform distribution of their heat exchange performance over their area. Inflow and outflow ports are at diagonally opposite corners of a rectangular substrate. In the vicinity of the inflow port, the temperature difference between the freshly supplied heat transfer fluid and a heat bath surrounding the heat exchanger is large, and accordingly the power density of the heat transfer between the heat transfer fluid and the heat bath is high. Towards the outlet connection, the temperature difference decreases, and accordingly, the power density of the heat exchanger decreases there as well.
  • the wall of the refrigeration appliance fitted with the heat exchanger would be substantially colder in the vicinity of the inflow connection than in the vicinity of the outflow connection.
  • a resulting uneven Temperature distribution in the storage room of the refrigeration device can sometimes lead to excessive and elsewhere insufficient cooling of the refrigerated goods.
  • the object of the present invention is to provide a heat exchanger having a two-dimensionally branched line structure which, when used in a refrigeration device, enables a more uniform distribution of the cooling capacity over the surface of the heat exchanger or a wall of the refrigeration device equipped with the heat exchanger.
  • the object is achieved by arranging, in a heat exchanger having a two-dimensionally branched line structure for a heat transfer fluid comprising an inflow connection and an outflow connection of a plurality of branching and joining points, the merging points at least with a predominant number in an outer edge region of the line structure a running in the edge region manifold are connected.
  • Fresh refrigerant fed into the heat exchanger therefore first cools a core region of the heat exchanger and spreads from there to the edge region.
  • a possible temperature gradient therefore does not extend diagonally, i. over the largest dimension of the line structure, but results in a temperature distribution, in which the temperature increases from the most cooled core area in different directions towards the edge area.
  • the distance between the warmest and coldest points is therefore significantly smaller than in a conventional heat exchanger with a branched line structure, and a resulting uneven distribution of the cooling capacity affects less in the storage room of the refrigerator due to the reduced distance between the warmest and the coldest places.
  • all joining points are arranged in an outer edge region of the line structure.
  • the manifold extends in the edge region up to the inflow port, so that the inflow port can be realized in known per se of heat exchangers with unbranched line structure forth as a guided inside the outflow port line. This simplifies the installation of the heat exchanger in a refrigeration device, since only at one point of the heat exchanger other parts of the refrigerant circuit leading lines must be connected.
  • the branched conduit structure defines a plurality of paths between the inflow port and the outflow port. If the narrowest points of these paths define a boundary between the edge region and the core region of the line structure containing the branching points, the boundary preferably forms an at least substantially closed curve so that the relatively warm edge region completely or almost completely surrounds the more cooled core region.
  • An open location of the boundary forming curve may be at the inflow port, especially if it is provided at an edge of the two-dimensional branched conduit structure.
  • the boundary may also form a fully closed curve.
  • the different paths between inflow and outflow ports are not necessarily all the same length.
  • the narrowest points of the paths are the narrower, the shorter these paths are.
  • the inflow port comprises a conduit guided within the outflow port
  • the narrowest points of the paths are expediently closer the closer these narrowest points are to the inflow port.
  • the distance between two adjacent conduit sections connecting upstream and downstream branching points is greater than between two adjacent conduit sections connecting one of these downstream branching points to an even further downstream branching point or point.
  • the distance between the pipe sections becomes smaller and smaller as the pipe structure ramifies.
  • the cross section of an upstream connecting with a downstream branch point Line section to be greater than the cross section of the outgoing from this upstream branch point line section.
  • the narrowest point of each path connecting the inflow port and the outflow port is preferably in a conduit section connecting a branch point and a merge point.
  • Fig. 1 illustrates the basic principle of the heat exchanger according to the invention with reference to a representation of a plant leaf and a schematic drawing of the evaporator.
  • Fig. 2 shows an evaporator according to the invention with a rectangular substrate.
  • Fig. 3 shows a modification of the evaporator of Fig. 2;
  • Fig. 4 shows a schematic perspective view of an inventive evaporator with central injection.
  • the system of the cores 2 comprises a straight axis extending the stem guide axis 3, distributed over its length and departing at its root branch veins 4. With increasing distance from the leading axis 3, the branch wires 4 branch one or more times.
  • the heat exchanger 11 shown schematically in FIG. 1 adopts the branching line structure of the plant leaf 1, but is fundamentally different from the plant leaf 1 in that a heat transfer fluid supplied at an inflow port 12 can not evaporate like the leaf 1 fed water, but via a drain port 13 must be derived again.
  • the aerodynamic vein structure of the plant leaf 1 can be transferred to the heat exchanger 11 by providing a collecting line 14 as the outer edge of its line structure.
  • the piping structure of the heat exchanger 11 may be understood as a tree structure having a first order branch point 15, first order piping 16 directly connecting with the inflow port, connecting the first order branch point to a second order branch point 17, each of which has a plurality of second pipe sections Order 18 go out. This ramification continues until lead portions of the last order at a merge point 19 in the manifold 14.
  • the line section of the last order may in individual cases be a second-order section 18, a fourth-order section 20 or a section of any other order.
  • the free cross sections of the n-th order line sections emanating from a nth-order branch point are smaller than the free cross section of the n-first order line section leading to the branch point, however, the sum of the cross sections of the line sections outgoing from a branch point is n-th Order larger than the cross section of the incoming n-1ter order line section, so that the flow velocity of the circulating in the line sections refrigerant with increasing order of Line sections decreases.
  • the gaps between adjacent line sections of equal, lower order are on average larger than between such higher orders, it is achieved that the heat exchange between the refrigerant and the environment increases in intensity with increasing order of the line sections.
  • the heat exchange performance is locally directly proportional to the temperature difference between the refrigerant and the environment, in a hypothetical unbranched heat exchanger with a constant line cross section neglecting countercurrent heating, the temperature of the refrigerant over the line length would match exponentially to the environment, so that a downstream line section considerably Contributes less to the total exchange rate than a section of equal length close to the inflow terminal.
  • the lines are increasingly branching out, but on the other hand the overall cross-section increasing in size leads to a lower flow velocity of the refrigerant in the higher-order line sections, the distribution of the heat exchange performance over the expansion of the heat exchanger is made uniform.
  • the manifold 14 extends into two arcs of gradually increasing cross-section from a tip 21 of the conduit structure opposite the ports 12, 13 to the drain port 13.
  • the two arcs of the manifold 14 may be connected at the tip 14, but this is not mandatory.
  • Fig. 2 shows a plan view of a heat exchanger according to the invention 1 1, which can be used as an evaporator in a refrigerator.
  • the line structure of the evaporator is formed in a manner known per se, in that two sheets, a flat sheet metal and one in which the line structure is impressed, are connected to one another in a flat manner.
  • the inflow port 12 here comprises a capillary 22 which extends within a suction pipe 23 emanating from the outflow port 13 in order to pre-cool refrigerant supplied in liquid form via the capillary 22 in thermal contact with gaseous refrigerant circulating in the intake manifold 23.
  • the capillary 22 opens into a zero-order line section 24 of large cross-section, in which the refrigerant evaporates and thus cools.
  • the refrigerant is distributed in an increasingly branching from the line section 24 of line structure, the line sections 16, 18, ... with increasing Keep getting tighter and closer and closer to each other.
  • 17 outgoing line sections may have very different cross-sections, depending on how large the part of the area of the heat exchanger to be supplied over the respective line section. For example, a line section that forms part of the main vein is always stronger than sections of the same order of branch veins.
  • the narrowest duct or narrowest duct section lies immediately upstream of the manifold 14 extending along the entire edge of the heat exchanger.
  • the dashed line curve 25 thus obtained marks a boundary between a core region 26 of the evaporator, in which an efficient heat exchange takes place, and an edge region 27, whose temperature is largely equal to the ambient temperature and therefore only slightly to the total cooling capacity of the Evaporator contributes.
  • the boundary 25 between the core region 26 and the edge region 27 can be defined as a closed curve, that is, the efficiently cooling core region 26 is surrounded on its entire circumference by the less efficient edge region 27.
  • FIG. 4 A further development of this design principle is shown in FIG. 4 in a schematic perspective view.
  • the capillary 22 opens centrally from above into a branching point of the first order 15, which forms the geometric center of the evaporator plate. From this branching point 15 go four first-order line sections 16, each of which supply by dash-dotted lines delimited triangular faces of the heat exchanger with refrigerant.
  • the location of the higher order branch points and the line sections connecting them is determined according to the algorithm known from EP 1 525 428 B1, however, since the area to which the algorithm is applied is triangular instead of rectangular as in the prior art, all the line sections highest order, instead of rejoining in pairs in a conventional manner, in which run out along the entire edge of the heat exchanger manifold 14.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L’invention concerne un échangeur de chaleur (11) à structure de conduites ramifiée bidimensionnelle pour un fluide caloporteur, cette structure comportant une pluralité de points de ramification et de réunion (15, 17, 19) entre un branchement de flux entrant (12) et un branchement de flux sortant (13). Selon l’invention, les points de réunion (19) sont tous disposés dans une zone de bord extérieure (27) de la structure de conduites, et reliés par l’intermédiaire d’une conduite collectrice (14) s’étendant dans la zone de bord (27).
EP09706056A 2008-01-29 2009-01-14 Échangeur de chaleur à structure de conduites fractale Withdrawn EP2238401A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810006513 DE102008006513A1 (de) 2008-01-29 2008-01-29 Wärmetauscher
PCT/EP2009/050384 WO2009095305A1 (fr) 2008-01-29 2009-01-14 Échangeur de chaleur à structure de conduites fractale

Publications (1)

Publication Number Publication Date
EP2238401A1 true EP2238401A1 (fr) 2010-10-13

Family

ID=40463857

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09706056A Withdrawn EP2238401A1 (fr) 2008-01-29 2009-01-14 Échangeur de chaleur à structure de conduites fractale

Country Status (5)

Country Link
EP (1) EP2238401A1 (fr)
CN (1) CN101932899A (fr)
DE (1) DE102008006513A1 (fr)
RU (1) RU2010134817A (fr)
WO (1) WO2009095305A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011117928A1 (de) * 2011-09-19 2013-03-21 Bundy Refrigeration Gmbh Mehrkanal-Verdampfersystem
DE102012101186A1 (de) * 2012-02-15 2013-08-22 Karlsruher Institut für Technologie Wärmetauscherstruktur
CN103968695A (zh) * 2014-05-27 2014-08-06 哈尔滨工业大学 具有树形定向导热翅片结构的储能装置
CN107152797A (zh) * 2017-07-11 2017-09-12 石同生 单管口多分支自然循环管式集热器
CN111336724A (zh) * 2020-03-09 2020-06-26 云南师范大学 一种用于浸入式静态制冰微管蒸发器的汇流装置
CN112594058A (zh) * 2020-12-15 2021-04-02 吉安市裕财机械工程有限公司 一种柴油发电机装置
CN112539105A (zh) * 2020-12-15 2021-03-23 吉安市裕财机械工程有限公司 一种柴油发电机的散热系统

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1075645B (de) * 1960-02-18 LICENTIA Patent Verwaltungs GmbH Frankfurt/M Tiefkuhltruhe mit getrenntem Getrier und Lagerfach
DE1083836B (de) * 1957-12-24 1960-06-23 Licentia Gmbh Platten- oder Kastenverdampfer fuer Kaelteanlagen, insbesondere Kuehlschraenke
DE1476988A1 (de) * 1966-06-18 1970-03-19 Bosch Hausgeraete Gmbh Verdampfer fuer Kuehlgeraete,insbesondere fuer Haushalts-Kuehlschraenke
FR2549585A1 (en) * 1983-07-21 1985-01-25 Axergie Sa Evaporator for an installation with a closed thermodynamic loop for the flow of a working fluid, and installation incorporating this evaporator
JPH08247576A (ja) * 1995-03-14 1996-09-27 Toshiba Corp 空気調和装置
WO2001095688A1 (fr) * 2000-06-05 2001-12-13 The State Of Oregon Acting By And Through The State Board Of Higher Education On Behalf Of The University Of Oregon Appareil de transport a echelle variable et procedes correspondants
DE10319367A1 (de) 2003-04-29 2004-11-25 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Verfahren zur Erstellung eines Hydrauliknetzwerkes für einen optimierten Wärmeübertragungs- und Stofftransport

Non-Patent Citations (1)

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Title
See references of WO2009095305A1 *

Also Published As

Publication number Publication date
RU2010134817A (ru) 2012-03-10
CN101932899A (zh) 2010-12-29
WO2009095305A1 (fr) 2009-08-06
DE102008006513A1 (de) 2009-07-30

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