EP1106729A2 - Echangeur de chaleur à courants croisés pour sèche-linge avec condenseur - Google Patents

Echangeur de chaleur à courants croisés pour sèche-linge avec condenseur Download PDF

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Publication number
EP1106729A2
EP1106729A2 EP00119972A EP00119972A EP1106729A2 EP 1106729 A2 EP1106729 A2 EP 1106729A2 EP 00119972 A EP00119972 A EP 00119972A EP 00119972 A EP00119972 A EP 00119972A EP 1106729 A2 EP1106729 A2 EP 1106729A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
cross
flow heat
exchanger according
flow
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
EP00119972A
Other languages
German (de)
English (en)
Other versions
EP1106729B1 (fr
EP1106729A3 (fr
Inventor
Alexander Maute
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.)
Joma Polytec Kunststofftechnik GmbH
Original Assignee
Joma Polytec Kunststofftechnik 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
Priority claimed from DE19958106A external-priority patent/DE19958106B4/de
Application filed by Joma Polytec Kunststofftechnik GmbH filed Critical Joma Polytec Kunststofftechnik GmbH
Publication of EP1106729A2 publication Critical patent/EP1106729A2/fr
Publication of EP1106729A3 publication Critical patent/EP1106729A3/fr
Application granted granted Critical
Publication of EP1106729B1 publication Critical patent/EP1106729B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F28D9/0031—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 paired plates touching each other
    • F28D9/0037—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 paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00—Domestic laundry dryers
    • D06F58/20—General details of domestic laundry dryers 
    • D06F58/24—Condensing arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F28F21/065—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material the heat-exchange apparatus employing plate-like or laminated conduits
    • 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

Definitions

  • the invention relates to cross-flow heat exchangers for Condensation clothes dryer in one embodiment, such as they explained in the preamble of claims 1 and 2 and from DE 198 38 525 A1 are known.
  • Such a cross-flow heat exchanger stands out according to the invention by the characterizing features of Claims 1 and 2 respectively.
  • the webs on one or both sides of the Heat exchanger plates can be provided, depending on whether this to be oriented in a horizontal or vertical position.
  • the efficiency of the heat exchanger according to claim 1 improve significantly by the fact that Moist air duct is formed as a flat tube, whereby one whose pocket-like webs with a horizontal arrangement of Heat exchanger plates expedient only to the upper one Form pipe flat side.
  • the lower plate side of a heat exchanger plate on the of the heat exchanger plate underneath upwards protruding webs, so that despite the absence of the Bottom of the plate protruding downwards between Heat exchanger plates cooling air channels available and thus the Prerequisites for intensive heat dissipation created are.
  • the length of the extending across the moist air duct Ridges can be roughly the width of a flat tube trained moist air duct correspond. Is preferred however, a web length that is only a fraction of the Corresponds to the width of the flat tube, the webs in Longitudinal direction of the flat tube expediently on gap are provided offset to each other.
  • this heat exchanger construction it may be advantageous to use the webs at least over one Area of the flat tube wall part to the flow direction of the Cooling air directed obliquely, if necessary still densified in some areas or over the entire area flat tube wall part to each other in a symmetrical Provide inclined arrangement.
  • heat exchanger plates or the forming films of heat exchangers according to claims 1 and 2 are different materials, such as plastic or aluminum, as well as various manufacturing processes. If plastic film is used for plate production, see above is this e.g. thermally so that two for example, independent of each other, one each Halves forming plate part arise, which are in each other To bring cover and then to opposite Long sides to be welded tightly, glued or to be pressurized.
  • the two plate parts provide plastic films from one piece and by folding the plastic film the two plate parts to coincide with each other and then only along two overlapping longitudinal edge parts with each other by welding, gluing or pressure joining connect.
  • a preferred manufacturing method consist of heat exchanger plates in a blow mold molded from an extruded plastic tube.
  • plastic plate parts especially acrylonitrile-butadiene-styrene copolymers (ABS) or Polypropylene, where desired to achieve Cooling capacities or the necessary Thermal conductivity and stability a film thickness between 0.15 mm and 0.50 mm, preferably 0.30 mm, as advantageous has proven.
  • ABS acrylonitrile-butadiene-styrene copolymers
  • Polypropylene where desired to achieve Cooling capacities or the necessary Thermal conductivity and stability a film thickness between 0.15 mm and 0.50 mm, preferably 0.30 mm, as advantageous has proven.
  • the plate package 10 shown in Fig. 1 for a Cross-flow heat exchanger for condensation tumble dryers is, for example, eight individual ones, as a whole designated 12, for example horizontally one above the other stacked heat exchanger plates formed.
  • Each heat exchanger plate 12 each have, for example three moist air channels 14 running parallel to one another on that define flat tubes.
  • Each heat exchanger plate 12 consists of a lower plate part 16 (Fig. 4) and a upper plate part 18 (Fig. 3), which from a corresponding deformed film are formed.
  • thermoplastic plastic e.g. a film thermoplastic plastic. It might as well be one Foil made of suitable metal, for example aluminum, for Come into play.
  • the two plate parts 16 and 18, as shown in FIG. 7, can also be formed by a plastic film preformed in one piece as a blister, the halves of which then brought to congruence by folding and therefore only have to be welded along two overlapping longitudinal edge parts 30 and 31, for example.
  • the two duct wall parts 24 and 26 of the flat tubes Forming moist air channels 14 are transverse to Flow direction of the moist air is corrugated, wherein both wavy lines preferably parallel to each other run. This measure creates one accordingly Enlarged surface of the cooling capacity which increases the cooling capacity Channel wall parts 24 and 26.
  • the cooling fins 32 are, as shown in FIG. 6, through Thermoforming pocket-like, open to the moist air duct 14, molded so that the slat longitudinal wall parts 34 and 36 are at a mutual distance from each other, whereby these are preferably still slightly curved outwards are trained to the flow behavior in the To optimally design cooling channels 42.
  • cooling fins 32 By deep drawing the cooling fins 32, these are also rounded end edges 38 and 40 (Fig. 2) provided what has a favorable effect on the flow through cooling air.
  • the web-like cooling fins 32 in Comparison to those from a plastic film shaped, have a reduced height to prevent tearing to avoid the metal foil.
  • the cooling air is in through the heat exchanger plate pack 10 in the cooling air ducts 42 (FIG. 6) passed through.
  • the cooling air flows around the cooling fins 32 and brushes the undulating outer surface of the lower and upper plate part 16 and 18, the configuration the same is designed so that with a minimal height of the Heat exchanger plate package 10 an optimal Dehumidification performance, e.g. 0% residual moisture, is achieved (1: 1 exchanger).
  • Cooling fins 33 can, as shown in Fig. 9, e.g. symmetrical to the transverse center of the cooling air duct 42 under one Angle be inclined, if necessary with increasing lateral distance from the center of the channel enlarged.
  • Bars 32 or bar groups can be one on the cooling air side significant increase in cooling performance through the optimal Achieve exposure to the cooling surface. It can be so in the case of design-related, unfavorable installation conditions of the heat exchanger in the housing Condensation washer dryer by appropriate choice of for air routing and for swirling the cooling air leading pitch angle and by the number of webs 32 to be inclined compared to parallel directed webs 32 up to 20% more cooling capacity to reach.
  • the heat exchanger plate pack 10 is, analogously to Construction of DE 198 38 525 A1 cited above, at its both ends in one made of plastic existing holding frame sealed what is using an adhesive, preferably cast resin, can be accomplished.
  • the heat exchanger plate package 10 on both sides against a punched or punched Soft rubber sheets are pressed in the relevant Holding frame is inserted.
  • Heat exchanger plate pack and holding frame Another advantageous way of connecting Heat exchanger plate pack and holding frame can be in it exist, the heat exchanger plates with each end to weld a holding frame.
  • FIG. 10 illustrates heat exchanger plate in its Cross-sectional design essentially corresponds to that 3 to 5, but with the Difference that they are rather than by each other plastic films connected in a vapor-tight manner Plastic existing molded body 44 is formed from one piece is made by blowing.
  • This manufacturing method largely enables one scrap-free manufacturing process.
  • 11 to 14 illustrate a plate pack 50 for a cross-flow heat exchanger according to claim 2. Accordingly the cooling air through its heat exchanger plates 52nd passed while the humid air Moist air channels 54 flows between the Heat exchanger plates 52 are present.
  • the end of the heat exchanger plates 52 is in a holding frame 56 indicated by dash-dotted lines or 58 sealed, which they with their Push through cooling air duct 60.
  • Cooling air is preferably corrugated parallel to one another trained, whereby a correspondingly enlarged Cooling surface is achieved.
  • the wave profile is preferably chosen such that the bottom 66 of the wave valleys about halfway up the Cooling air channels 60 is located (see FIG. 13), whereby a correspondingly strong exposure to the corrugated Channel inner surfaces for effective heat dissipation is ensured.
  • the wave profile can be transverse to the direction of flow Cooling air seen also run asymmetrically, d. i.e., the Rise phase in the direction of flow flatter and the Fall phase steeper. This allows the pressure drop reduce and flow separations on the sloping Avoid page largely.
  • Wave crests 68 of the lower plate part 64 of the Heat exchanger plates 52 each have a variety of laterally spaced apart, elongated depressions 70 molded in, which is transverse to the longitudinal direction of the Wave crests 68 and up to the division plane a-a Extend heat exchanger plates 52 and to the wet air channel 54 located below each open Make pockets.
  • each two aligned Recesses 70 are provided, whereby relative to FIG. 13 long spacers are formed on which the Troughs of the upper plate part 62 with their base 66 support.
  • the spacers formed by the recesses 70 thus contribute to the stabilization and stiffening of the preferably from a thin-walled plastic film existing plate parts 62 and 64 as shown in FIG. 13 vertically to the direction of flow of those guided in their channel 60 Cooling air and also form in the interior of the duct Cooling elements extending in the direction of flow.
  • Analogous to the heat exchanger plates 12 in FIGS. 1 to 10 can the plate parts 62 and 64 molded or in Blow process to be made.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Drying Of Solid Materials (AREA)
EP00119972A 1999-12-02 2000-09-14 Echangeur de chaleur à courants croisés pour sèche-linge avec condenseur Expired - Lifetime EP1106729B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19958106A DE19958106B4 (de) 1999-08-20 1999-12-02 Kreuzstrom-Wärmetauscher Kondensationswäschetrockner und Verfahren zu dessen Herstellung
DE19958106 1999-12-02

Publications (3)

Publication Number Publication Date
EP1106729A2 true EP1106729A2 (fr) 2001-06-13
EP1106729A3 EP1106729A3 (fr) 2002-02-13
EP1106729B1 EP1106729B1 (fr) 2003-07-23

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EP00119972A Expired - Lifetime EP1106729B1 (fr) 1999-12-02 2000-09-14 Echangeur de chaleur à courants croisés pour sèche-linge avec condenseur

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EP (1) EP1106729B1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1550835A2 (fr) 2003-11-27 2005-07-06 Joma-Polytec Kunststofftechnik GmbH Echangeur de chaleur à courants croisés pour sèche-linge avec condenseur
DE202007007169U1 (de) * 2007-05-16 2008-09-25 Akg-Thermotechnik Gmbh & Co. Kg Wärmeaustauscher für gasförmige Medien
CN100451230C (zh) * 2003-04-11 2009-01-14 乐金电子(天津)电器有限公司 冷凝式衣类烘干机的冷凝器的结构
WO2012136432A1 (fr) * 2011-04-07 2012-10-11 Alfa Laval Corporate Ab Échangeur de chaleur à plaques
CN109892995A (zh) * 2019-04-02 2019-06-18 浙江蓝炬星电器有限公司 一种用于嵌入式蒸烤箱安装的通风装置及其施工方法
WO2021069386A1 (fr) 2019-10-10 2021-04-15 Thyssenkrupp Industrial Solutions Ag Séparation d'eau à partir des gaz de fumée issus d'installation de cuisson de clinker
CN114945792A (zh) * 2020-01-14 2022-08-26 大金工业株式会社 板壳式热交换器
EP4023997A4 (fr) * 2019-11-06 2022-12-14 Huawei Digital Power Technologies Co., Ltd. Plaque d'échange de chaleur et échangeur de chaleur la comprenant

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2462421A (en) * 1944-10-26 1949-02-22 Solar Aircraft Co Crossflow heat exchanger
FR1567831A (fr) * 1967-06-08 1969-04-08
US3859025A (en) * 1972-07-13 1975-01-07 Ernest J Maroschak Apparatus for making corrugated plastic pipes with integral coupler collar
DE2340003A1 (de) * 1973-08-07 1975-02-20 Linde Ag Entnebelungsvorrichtung
DE2167014A1 (de) * 1971-08-12 1977-06-23 Buderus Eisenwerk Im blasverfahren hergestellter heizkoerper aus kunststoff
FR2335813A1 (fr) * 1975-12-19 1977-07-15 Hisaka Works Ltd Condenseur
US4119144A (en) * 1975-11-24 1978-10-10 Union Carbide Corporation Improved heat exchanger headering arrangement
EP0625688A1 (fr) * 1993-05-18 1994-11-23 SGL Technic Echangeur de chaleur à plaques
EP0658735B1 (fr) * 1993-12-18 1997-02-12 BDAG Balcke-Dürr Aktiengesellschaft Echangeur de chaleur à plaques
DE19838525A1 (de) * 1997-09-03 1999-03-04 Joma Polytec Kunststofftechnik Kreuzstrom-Wärmetauscher für Kondensationswäschetrockner
FR2777644A1 (fr) * 1998-04-21 1999-10-22 Valeo Thermique Moteur Sa Echangeur de chaleur de vehicule automobile comprenant un faisceau de tubes paralleles plats en materiau thermoplastique preforme, et son procede de fabrication

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2462421A (en) * 1944-10-26 1949-02-22 Solar Aircraft Co Crossflow heat exchanger
FR1567831A (fr) * 1967-06-08 1969-04-08
DE2167014A1 (de) * 1971-08-12 1977-06-23 Buderus Eisenwerk Im blasverfahren hergestellter heizkoerper aus kunststoff
US3859025A (en) * 1972-07-13 1975-01-07 Ernest J Maroschak Apparatus for making corrugated plastic pipes with integral coupler collar
DE2340003A1 (de) * 1973-08-07 1975-02-20 Linde Ag Entnebelungsvorrichtung
US4119144A (en) * 1975-11-24 1978-10-10 Union Carbide Corporation Improved heat exchanger headering arrangement
FR2335813A1 (fr) * 1975-12-19 1977-07-15 Hisaka Works Ltd Condenseur
EP0625688A1 (fr) * 1993-05-18 1994-11-23 SGL Technic Echangeur de chaleur à plaques
EP0658735B1 (fr) * 1993-12-18 1997-02-12 BDAG Balcke-Dürr Aktiengesellschaft Echangeur de chaleur à plaques
DE19838525A1 (de) * 1997-09-03 1999-03-04 Joma Polytec Kunststofftechnik Kreuzstrom-Wärmetauscher für Kondensationswäschetrockner
FR2777644A1 (fr) * 1998-04-21 1999-10-22 Valeo Thermique Moteur Sa Echangeur de chaleur de vehicule automobile comprenant un faisceau de tubes paralleles plats en materiau thermoplastique preforme, et son procede de fabrication

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100451230C (zh) * 2003-04-11 2009-01-14 乐金电子(天津)电器有限公司 冷凝式衣类烘干机的冷凝器的结构
EP1550835A2 (fr) 2003-11-27 2005-07-06 Joma-Polytec Kunststofftechnik GmbH Echangeur de chaleur à courants croisés pour sèche-linge avec condenseur
EP1550835A3 (fr) * 2003-11-27 2006-10-04 Joma-Polytec Kunststofftechnik GmbH Echangeur de chaleur à courants croisés pour sèche-linge avec condenseur
DE202007007169U1 (de) * 2007-05-16 2008-09-25 Akg-Thermotechnik Gmbh & Co. Kg Wärmeaustauscher für gasförmige Medien
WO2012136432A1 (fr) * 2011-04-07 2012-10-11 Alfa Laval Corporate Ab Échangeur de chaleur à plaques
CN109892995A (zh) * 2019-04-02 2019-06-18 浙江蓝炬星电器有限公司 一种用于嵌入式蒸烤箱安装的通风装置及其施工方法
WO2021069386A1 (fr) 2019-10-10 2021-04-15 Thyssenkrupp Industrial Solutions Ag Séparation d'eau à partir des gaz de fumée issus d'installation de cuisson de clinker
EP4023997A4 (fr) * 2019-11-06 2022-12-14 Huawei Digital Power Technologies Co., Ltd. Plaque d'échange de chaleur et échangeur de chaleur la comprenant
CN114945792A (zh) * 2020-01-14 2022-08-26 大金工业株式会社 板壳式热交换器
CN114945792B (zh) * 2020-01-14 2023-12-22 大金工业株式会社 板壳式热交换器

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Publication number Publication date
EP1106729B1 (fr) 2003-07-23
EP1106729A3 (fr) 2002-02-13

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