EP0211400A1 - Echangeur de chaleur à plaques - Google Patents

Echangeur de chaleur à plaques Download PDF

Info

Publication number
EP0211400A1
EP0211400A1 EP86110554A EP86110554A EP0211400A1 EP 0211400 A1 EP0211400 A1 EP 0211400A1 EP 86110554 A EP86110554 A EP 86110554A EP 86110554 A EP86110554 A EP 86110554A EP 0211400 A1 EP0211400 A1 EP 0211400A1
Authority
EP
European Patent Office
Prior art keywords
plates
heat exchanger
exchanger body
plate heat
corrugated
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
EP86110554A
Other languages
German (de)
English (en)
Other versions
EP0211400B1 (fr
Inventor
Heinz Dr.-Ing. Gross
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.)
Roehm GmbH Darmstadt
Original Assignee
Roehm GmbH Darmstadt
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 Roehm GmbH Darmstadt filed Critical Roehm GmbH Darmstadt
Publication of EP0211400A1 publication Critical patent/EP0211400A1/fr
Application granted granted Critical
Publication of EP0211400B1 publication Critical patent/EP0211400B1/fr
Expired legal-status Critical Current

Links

Images

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
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/356—Plural plates forming a stack providing flow passages therein
    • Y10S165/393—Plural plates forming a stack providing flow passages therein including additional element between heat exchange plates
    • Y10S165/394—Corrugated heat exchange plate

Definitions

  • the invention relates in a broader sense to a plate heat exchanger, in the narrower sense to a plate heat exchanger body.
  • Plate heat exchangers consist of a stack of corrugated plates between which channels can flow. The area in which heat is exchanged between these channels is the actual heat exchanger body, while the complete heat exchanger also includes a system of supply and discharge lines to the individual channels for the flowing media.
  • the invention relates primarily to a new design of the plate heat exchanger body, which can be equipped in a conventional manner with supply and discharge lines for the flowing media.
  • Known plate heat exchangers (according to Ullmann, Encyclopedia of Technical Chemistry, 4th edition, volume 2, p. 440) consist of a bundle of any number of corrugated or otherwise profiled plates, which are separated from one another by seals and held together in a press. After opening the press, plates can be easily removed from separate and clean each other.
  • So-called lamella or stacked heat exchangers are composed of a stack of alternately flat and corrugated sheets, the direction of corrugation of the corrugated sheets alternating.
  • a collecting box and a feed or discharge line for the flowing media are attached to the four side surfaces of the stack.
  • the media between which heat is exchanged can only be routed crosswise to one another. The heat transfer takes place only on the flat sheets.
  • Plate or finned heat exchangers are inexpensive due to their simple construction and easy to maintain and clean due to their easy removal and installation.
  • the invention has for its object to improve the effectiveness of plate heat exchanger bodies, consisting of a stack of corrugated plates, between which flow-through channels exist, with a consistently simple structure.
  • the heat exchanger body according to the invention is composed of plates which are corrugated at least in partial areas in two mutually cross-lying directions. In the stack of successive plates are arranged in such a way that the corrugations in the cross-corrugated areas or partial areas are in phase in one direction and in phase opposition in the other direction.
  • the plates used for the construction of the heat exchanger body are easy to produce, since they are single-surface bodies without ribs or protrusions protruding from the surface, which can be easily produced by known methods by shaping a flat surface material.
  • a plurality of parallel channels which can be flowed through by a liquid or gaseous medium, automatically results between two plates.
  • These channels have a corrugated course, which strongly swirls the flowing medium.
  • a turbulent boundary layer is formed even at low flow velocities, which leads to an increase in the heat transfer coefficient.
  • the crosswise corrugation of the plate segments results in a considerable increase in the surface area available for heat exchange.
  • the heat exchange is further promoted in that all channel walls are touched by the other medium, so that there are practically no ineffective walls for heat exchange between the channels through which the same medium flows.
  • each individual plate Due to the biaxial corrugation, each individual plate has a high level of rigidity, which is increased considerably when assembled into a stack, since all individual plates are mutually supported at short intervals. Therefore, even when thin-walled material is used for the individual plates, a mechanically extremely stiff and stable heat exchanger body of low weight and high exchange capacity is obtained.
  • the heat exchanger according to the invention is suitable for heat exchange between liquid or gaseous media or between a liquid and a gaseous medium. It is particularly suitable for the creation of large heat exchange systems, especially in cooling towers, where a large number of heat exchanger bodies are combined to form a large cooling system.
  • the heat exchanger body can also serve as a chemical reactor at the same time if the channels are filled in one direction with a flowable catalyst mass or their walls are covered with a catalyst material.
  • the channels can also be filled with flowable absorption materials, so that the heat exchanger body also acts as a filter.
  • the simple production method of the heat exchanger body makes it possible to achieve any desired dimensioning and any desired adaptation to the temperatures occurring during operation and the chemical nature of the flowing media.
  • the surface shape of the biaxially corrugated plate arises from the fact that a wave curve E as generatrix is shifted in parallel on a wave-shaped guide curve F.
  • the roles of the leadership curve and the generators are interchangeable.
  • Each intersection that is parallel to the generatrix E through the biaxial corrugated surface has the profile of the generatrix E.
  • each intersection that is parallel to the guide curve F through the biaxially corrugated surface has the profile of the guide curve F.
  • domes 4 and troughs 5 result from the superimposition of the two wave trains, between which saddle surfaces lie, the highest and lowest points of which are at a height level that is the middle between the level of the domes 4 and the level the trough 5 forms.
  • the two corrugation axes E and F are generally at right angles to one another, but this is not a mandatory requirement for the construction of the heat exchanger body. It is also expedient, but not essential, that the wave trains E and F coincide in the wave form, the wavelength and the wave amplitude.
  • the waveform is chosen so that two in-phase waves can be joined as closely as possible.
  • Sine waves, trapezoidal waves and intermediate wave types are suitable, the individual waves of which can be composed of curved and bent straight-line pieces.
  • a trapezoidal curve was used as the basis for the wave curves E and F in FIGS.
  • the channels form automatically when the biaxially corrugated plates are stacked in the manner according to the invention. Therefore, the outer boundary of the individual plates is basically arbitrary. However, in order to be able to easily attach the feed and discharge line, it is expedient that all plates have the same base area so that they form a common side surface in the stack. A rectangular base is useful.
  • the wavelength and the wave amplitude depend both on the intended use of the heat exchanger body and on the method of manufacture of the plates.
  • the ratio of wave amplitude to wavelength is preferably in the range from 1:10 to 1: 1. A high ratio within this range promotes a strong swirling of the flowing medium and thus good heat transfer, but leads to a high flow resistance. With a decreasing ratio of amplitude to wavelength, the flow resistance initially decreases, but then increases again due to the narrowing of the channel cross section.
  • the wavelength is preferably in the range of 10 to 500 mm, the wave amplitude accordingly in the range from 1 to 150 mm.
  • the number of shafts in the longitudinal and transverse directions can be freely selected according to the technical requirements.
  • the lengths of the side edges of a rectangular base area are preferably 0.1 to 3 m and the number of waves on each side is approximately 10 to 400.
  • a variety of materials are suitable for the production of the biaxially corrugated plates.
  • metals ceramic materials such as clay, porcelain or glass, plastic, such as thermoplastics, thermosets, fiber-reinforced plastics or plastic-filled fabrics or nonwovens.
  • plastic such as thermoplastics, thermosets, fiber-reinforced plastics or plastic-filled fabrics or nonwovens.
  • Flat, flat starting materials that can be formed into the biaxially corrugated shape are particularly advantageous. This includes sheets of steel, aluminum, copper and other metals or alloys, as well as all thermoplastic or thermo-elastic plastic sheets. Suitable plastic panels of this type exist for. B.
  • Fiber-filled plastics such as so-called prepregs, which generally consist of a glass fiber fleece and a thermosetting epoxy resin, are also very suitable.
  • the sheet-like starting materials are brought into the desired biaxially corrugated shape under forming conditions between two suitable corresponding tools.
  • the circum ting plastics in the thermoelastic state it is not necessary to use fully developed molds. It is sufficient if the outermost maxima 4 and minima 5 are formed by suitable stamps.
  • the intermediate waveforms are automatically formed in the required manner under the influence of the elastic counterforces that arise during the deformation.
  • Plastic sheets with a thickness of 0.01 to 3 mm can be used for this deformation.
  • Metal sheets can also be unshaped in a corresponding manner.
  • a heat exchanger body with alternating layers of parallel channels for each of the two media is formed from three or more stacked biaxially corrugated plates. Each additional plate adds another layer of parallel flow channels.
  • the plates are stacked in such a way that the corrugations of two successive plates run in phase in the direction of one shaft axis and in phase opposition in the direction of the other shaft axis. Plates which have a uniform cross-corrugation throughout can be put together to form a cross-flow recuperator, with the directions of the in-phase and the antiphase course changing with each plate.
  • there are four different positions of the individual plates which are designated in Figure 3 with 1 to IV.
  • the position of the fifth plate matches the position of the first.
  • a cross-flow recuperator with side edges lying in one plane can be constructed from the desired number of completely identical individual plates. These are each offset by a quarter turn. This design is particularly advantageous because you can produce biaxially corrugated plates with a single pair of forming tools without waste, which can be brought into each of the four positions I to IV by quarter turns.
  • the cross-flow recuperator has the advantage that the supply lines 7, 8 and the discharge lines 9, 10 for two media flowing through can be connected to the heat exchanger body 15 in a particularly simple manner by placing a collecting box 11, 12, 13, 14 on each of its four side surfaces , of which two opposite boxes 11, 12 and 13, 14 each carry one of the two media.
  • Counterflow heat exchangers have a higher heat exchange line, in which all channels run in parallel in all layers.
  • This structure can be achieved in a simple manner according to the invention in that the surface elements are always stacked in phase in the same direction. In this case, however, the ends of the channels for both media lie alternately in layers on two opposite sides of the plate stack and have to be layered alternately connected to the respective supply lines.
  • This disadvantage can be avoided if the plates only in a central area 16, the z. B. occupies three quarters of the total area, have a crosswise corrugation.
  • the outer regions 17 adjoining on both sides can be undulating.
  • the plates are stacked in such a way that the channels are parallel to one another in all layers and lead from one outer region 17 to the opposite outer region.
  • the edge of the plates expediently forms a step 2 upwards in the one direction of the edge and a step 3 downwards in the other direction of the edge.
  • Successive plates in the stack are each opposed, which forms an inlet funnel 19 and 20 in each layer.
  • the funnel 19, which extends to the corners, is laterally closed at each corner of the stack of plates with an elastic sealing block 21.
  • 5 collection boxes 11, 12, 13, 14 are connected to the sides of the heat exchanger body 15 and the lines 7 and 9 as inlet and outlet for the one medium and the lines 8 and 10 as inlet and outlet for the other medium is used, a counter flow heat exchanger is obtained.
  • the inlet funnel 20 must be closed by a sealing profile 22 so that there is only access to the one outer area 17 from the connected collecting box 13, while there is only access to the other outer area from the other collecting box 14.
  • Fig. 4 shows an embodiment in which the plates 24 also are corrugated in the outer regions 17, whereby a larger surface area, a higher turbulence and a better heat transfer are also achieved in this region.
  • Every second plate 23 in the stack is evenly biaxially corrugated except for the edge regions 2, 3.
  • the corrugation in the superimposed plates runs in phase in both directions, so that no channels are formed, but the entire outer area can be freely flowed through at any point at the same distance.
  • the number of biaxially corrugated plates that are combined to form a heat exchanger body is basically arbitrary. In individual cases, it depends on the required heat exchange performance and the most appropriate design. Typical heat exchanger bodies have 3 to 100 individual surfaces.
  • the individual plates in the edge regions 2, 3 are connected to one another in a sealing manner. This can be done, for example, by an attached U-profile 28, which is placed over two outer edges.
  • FIG. 11 Another possibility for connecting a collecting tank 11 is shown in FIG. It can be placed over the side surfaces of the plate stack and in a suitable manner, for. B. by gluing, tightly attached.
  • the collecting box is preferably detachably fastened and the connection of the plates is also detachable.
  • the collecting box can - at least where it rests against the stack of plates elastic material and be attached with a drawstring 25.
  • the inlet funnels 19 can be stiffened by an inserted U-profile 26 with a passage opening 27 in order to be able to press the edges 2 tightly against one another. A tight seal between two superimposed edges 2 can also be achieved by means of an attached U-profile 28.

Landscapes

  • 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)
EP86110554A 1985-08-06 1986-07-30 Echangeur de chaleur à plaques Expired EP0211400B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE8522627U DE8522627U1 (de) 1985-08-06 1985-08-06 Plattenwärmetauscher
DE8522627U 1985-08-06

Publications (2)

Publication Number Publication Date
EP0211400A1 true EP0211400A1 (fr) 1987-02-25
EP0211400B1 EP0211400B1 (fr) 1988-11-02

Family

ID=6783936

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86110554A Expired EP0211400B1 (fr) 1985-08-06 1986-07-30 Echangeur de chaleur à plaques

Country Status (4)

Country Link
US (1) US4724902A (fr)
EP (1) EP0211400B1 (fr)
CA (1) CA1273005A (fr)
DE (2) DE8522627U1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1990013783A1 (fr) * 1989-05-01 1990-11-15 Stanislas Glomski Assemblage de parois pour echangeur thermique
WO2018067026A1 (fr) * 2016-10-04 2018-04-12 Deta Engineering Llc Échangeur de chaleur à plaques et conception d'unité d'étanchéité pour celui-ci

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8522627U1 (de) * 1985-08-06 1985-09-19 Röhm GmbH, 6100 Darmstadt Plattenwärmetauscher
US5228515A (en) * 1992-07-31 1993-07-20 Tran Hai H Modular, compact heat exchanger
AUPN123495A0 (en) * 1995-02-20 1995-03-16 F F Seeley Nominees Pty Ltd Contra flow heat exchanger
JPH09184692A (ja) * 1995-12-28 1997-07-15 Ebara Corp 熱交換エレメント
DE10049194A1 (de) * 2000-10-05 2002-04-11 Xcellsis Gmbh Raktorstruktur in Wärmeübertrager-Schichtstapelbauweise
US7476367B2 (en) * 2001-09-15 2009-01-13 Precision Combustion, Inc. Stacked catalytic reactor
US7328886B2 (en) * 2001-10-11 2008-02-12 Spx Cooling Technologies, Inc. Air-to-air atmospheric heat exchanger for condensing cooling tower effluent
JP2004028385A (ja) * 2002-06-24 2004-01-29 Hitachi Ltd プレート式熱交換器
DE10333177A1 (de) * 2003-07-22 2005-02-24 Modine Manufacturing Co., Racine Strömungskanal für einen Wärmeaustauscher
DE102005012000A1 (de) * 2005-03-16 2006-09-21 Mahle International Gmbh Plattenwärmetauscher
JP2006317029A (ja) * 2005-05-10 2006-11-24 Xenesys Inc 熱交換ユニット
JP2007010202A (ja) * 2005-06-29 2007-01-18 Xenesys Inc 熱交換ユニット
GB0622355D0 (en) * 2006-11-09 2006-12-20 Oxycell Holding Bv High efficiency heat exchanger and dehumidifier
FR2972130B1 (fr) * 2011-03-02 2014-05-23 Pierre Vironneau Feuille metallique pour echangeur thermique fluidique double flux, echangeur thermique fluidique double flux, et procedes de fabrication
GB201121754D0 (en) * 2011-12-19 2012-02-01 Rolls Royce Plc A heat exchanger
US9359952B2 (en) 2012-02-03 2016-06-07 Pratt & Whitney Canada Corp Turbine engine heat recuperator plate and plate stack
NL2017947B1 (nl) * 2016-12-07 2018-06-19 Recair Holding B V Recuperator
FR3105387B1 (fr) * 2019-12-20 2021-11-26 Liebherr Aerospace Toulouse Sas Échangeur de chaleur à passages de fluide optimisés
CN117650312B (zh) * 2024-01-30 2024-04-26 深圳市科瑞隆科技有限公司 一种耐高温的聚合物锂电池组

Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1328323A (en) * 1916-04-05 1920-01-20 Fedders Mfg Co Inc Radiator-core
US2288061A (en) * 1940-10-28 1942-06-30 Modine Mfg Co Oil cooler and heat exchanger
CH253573A (de) * 1945-05-28 1948-03-15 Ljungstroms Angturbin Ab Wärmeaustauschvorrichtung.
US2550339A (en) * 1948-08-03 1951-04-24 York Corp Plate type heat exchanger
FR990903A (fr) * 1948-07-16 1951-09-27 Separator Ab échangeur de chaleur cloisonné
GB821430A (en) * 1954-12-11 1959-10-07 Danske Mejeriers Maskinfabrik Improvements in and relating to methods of and apparatus for indirect heat exchange between two fluid media
US3119446A (en) * 1959-09-17 1964-01-28 American Thermocatalytic Corp Heat exchangers
GB954066A (en) * 1960-12-08 1964-04-02 Marston Excelsior Ltd Improvements relating to heat exchangers
US3291206A (en) * 1965-09-13 1966-12-13 Nicholson Terence Peter Heat exchanger plate
DE1551452A1 (de) * 1967-05-23 1970-05-06 Daimler Benz Ag Waermetauschermatrix aus in mehreren Lagen angeordneten Blechen
GB1223752A (en) * 1968-01-04 1971-03-03 Terence Peter Nicholson Heat exchanger
FR2318398A1 (fr) * 1975-07-18 1977-02-11 Munters Ab Carl Procede de realisation d'un corps d'echange de chaleur pour des echangeurs a recuperation
FR2377598A1 (fr) * 1977-01-14 1978-08-11 Munters Ab Carl Echangeur de chaleur a plaques
DE2910005A1 (de) * 1979-03-14 1980-09-18 Siemens Ag Waermetauscher
US4460388A (en) * 1981-07-17 1984-07-17 Nippon Soken, Inc. Total heat exchanger
US4470453A (en) * 1982-08-19 1984-09-11 Avco Corporation Primary surface for compact heat exchangers
DE8522627U1 (de) * 1985-08-06 1985-09-19 Röhm GmbH, 6100 Darmstadt Plattenwärmetauscher

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU800569A1 (ru) * 1979-04-26 1981-01-30 Куйбышевский Политехническийинститут Им. B.B.Куйбышева Тепломассообменный аппарат
DE3008717A1 (de) * 1980-03-07 1981-09-17 Witzenmann Gmbh Metallschlauch-Fabrik Pforzheim, 7530 Pforzheim Membran-waermetauscher
US4544513A (en) * 1983-04-15 1985-10-01 Arvin Industries, Inc. Combination direct and indirect evaporative media
SE8402163D0 (sv) * 1984-04-18 1984-04-18 Alfa Laval Food & Dairy Eng Vermevexlare av fallfilmstyp

Patent Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1328323A (en) * 1916-04-05 1920-01-20 Fedders Mfg Co Inc Radiator-core
US2288061A (en) * 1940-10-28 1942-06-30 Modine Mfg Co Oil cooler and heat exchanger
CH253573A (de) * 1945-05-28 1948-03-15 Ljungstroms Angturbin Ab Wärmeaustauschvorrichtung.
FR990903A (fr) * 1948-07-16 1951-09-27 Separator Ab échangeur de chaleur cloisonné
US2550339A (en) * 1948-08-03 1951-04-24 York Corp Plate type heat exchanger
GB821430A (en) * 1954-12-11 1959-10-07 Danske Mejeriers Maskinfabrik Improvements in and relating to methods of and apparatus for indirect heat exchange between two fluid media
US3119446A (en) * 1959-09-17 1964-01-28 American Thermocatalytic Corp Heat exchangers
GB954066A (en) * 1960-12-08 1964-04-02 Marston Excelsior Ltd Improvements relating to heat exchangers
US3291206A (en) * 1965-09-13 1966-12-13 Nicholson Terence Peter Heat exchanger plate
DE1551452A1 (de) * 1967-05-23 1970-05-06 Daimler Benz Ag Waermetauschermatrix aus in mehreren Lagen angeordneten Blechen
GB1223752A (en) * 1968-01-04 1971-03-03 Terence Peter Nicholson Heat exchanger
FR2318398A1 (fr) * 1975-07-18 1977-02-11 Munters Ab Carl Procede de realisation d'un corps d'echange de chaleur pour des echangeurs a recuperation
FR2377598A1 (fr) * 1977-01-14 1978-08-11 Munters Ab Carl Echangeur de chaleur a plaques
DE2910005A1 (de) * 1979-03-14 1980-09-18 Siemens Ag Waermetauscher
US4460388A (en) * 1981-07-17 1984-07-17 Nippon Soken, Inc. Total heat exchanger
US4470453A (en) * 1982-08-19 1984-09-11 Avco Corporation Primary surface for compact heat exchangers
DE8522627U1 (de) * 1985-08-06 1985-09-19 Röhm GmbH, 6100 Darmstadt Plattenwärmetauscher

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1990013783A1 (fr) * 1989-05-01 1990-11-15 Stanislas Glomski Assemblage de parois pour echangeur thermique
WO2018067026A1 (fr) * 2016-10-04 2018-04-12 Deta Engineering Llc Échangeur de chaleur à plaques et conception d'unité d'étanchéité pour celui-ci

Also Published As

Publication number Publication date
DE3661112D1 (en) 1988-12-08
EP0211400B1 (fr) 1988-11-02
DE8522627U1 (de) 1985-09-19
US4724902A (en) 1988-02-16
CA1273005A (fr) 1990-08-21

Similar Documents

Publication Publication Date Title
EP0211400B1 (fr) Echangeur de chaleur à plaques
DE69921584T2 (de) Füllkörper mit Filmströmung, mit Gaswirbelströmung für Kontaktvorrichtung mit Stoff- und Wärmeaustausch, mit Rieselplatten mit Distanzstücken
DE69317558T2 (de) Wellblechanordnung
DE2122537C3 (de) Flüssigkeitskühler
EP0167938B1 (fr) Corps échangeur de chaleur en matière plastique
DE3918483C2 (fr)
DE69302212T2 (de) Plattenstapel für Wärmetauscher und Verfahren zu dessen Zusammenbau
DE1601216B2 (de) Blechtafel fuer platten waermetauscher mit einem stapel solcher blechtafeln
DE2322683B2 (de) Einbauelement zur Flüssigkeitsführung in einem Naß- oder Rieselkfihlturm
EP0315052A1 (fr) Echangeur de chaleur à courants croisés fait de plastique
EP0044561A2 (fr) Echangeur de chaleur, particulièrement pour échange de chaleur entre fluides gazeux
DE2318462A1 (de) Waermeaustauscher
DE2701633A1 (de) Waermeaustauscher
DE19909881A1 (de) Wärmeübertrager in Kreuzstrom-Bauweise
DE2951352C2 (de) Flachrohr-Wärmetauscher
EP0065679A1 (fr) Elément plate et flexible pour échangeurs de chaleur
DE3102763A1 (de) Phasenkontaktiervorrichtung und packungen hierfuer
DE8607689U1 (de) Zu einem Plattenstapel verschweißbare Kunststoffplatte und daraus gefertigter Plattenstapel
EP0036944B1 (fr) Corps de garnissage
DE2165267A1 (de) Waermetauscher
DE2822376B2 (de) Tropfenabscheider
DE1287096B (de) Rieseleinbau fuer Kuehltuerme
DE2910005A1 (de) Waermetauscher
DE2831639C2 (de) Plattenbatterie für Stoff- und Wärmetauscher sowie für Tropfenabscheider
WO1985003564A1 (fr) Echangeur de chaleur en forme de plaque

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE FR GB LI NL SE

17P Request for examination filed

Effective date: 19870625

17Q First examination report despatched

Effective date: 19880105

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE FR GB LI NL SE

REF Corresponds to:

Ref document number: 3661112

Country of ref document: DE

Date of ref document: 19881208

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19920731

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19930731

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19930915

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19940731

Ref country code: CH

Effective date: 19940731

EUG Se: european patent has lapsed

Ref document number: 86110554.2

Effective date: 19930204

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19950201

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19950711

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19950719

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19950725

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19950727

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19960730

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19960730

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19970328

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19970402

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST