EP0449783A2 - Echangeur de chaleur, en particulier pour installation de ventilation - Google Patents

Echangeur de chaleur, en particulier pour installation de ventilation Download PDF

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Publication number
EP0449783A2
EP0449783A2 EP91810214A EP91810214A EP0449783A2 EP 0449783 A2 EP0449783 A2 EP 0449783A2 EP 91810214 A EP91810214 A EP 91810214A EP 91810214 A EP91810214 A EP 91810214A EP 0449783 A2 EP0449783 A2 EP 0449783A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger according
flow
surface elements
folded
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
EP91810214A
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German (de)
English (en)
Other versions
EP0449783A3 (en
EP0449783B1 (fr
Inventor
Friedrich Bachofen
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.)
Polybloc AG
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Polybloc AG
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 Polybloc AG filed Critical Polybloc AG
Publication of EP0449783A2 publication Critical patent/EP0449783A2/fr
Publication of EP0449783A3 publication Critical patent/EP0449783A3/de
Application granted granted Critical
Publication of EP0449783B1 publication Critical patent/EP0449783B1/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

Definitions

  • the invention relates to a heat exchanger, in particular for ventilation systems, consisting of surface elements of identical shape which are stacked at a distance from one another by means of inserted or molded spacers and which are bent at right angles twice in the same direction to form flow cross sections on the opposite sides, in each case rotated by 90 ° to one another, and the bevelled legs encompass the closest surface element, with three of these surface elements forming two adjacent flow channels with flow directions crossing each other at right angles.
  • Cross-flow heat exchangers are known for the heat transfer between two flow media. If the flow media are vapors or gases, larger exchange surfaces are required due to the significantly lower heat capacity and conductivity, especially with gases compared to liquids. For example, air must compensate for its low thermal conductivity in thin layers between the exchange surfaces if good heat transfer is to be achieved. In addition, a material with a small thermal capacity and high thermal conductivity is advantageous for the exchange surfaces.
  • heat exchangers for ventilation systems in industry are affected by other factors. For example, air supplied to heat exchangers often contains vaporous or solid substances that condense or deposit on the exchange surfaces. The efficiency of the heat exchanger is considerably reduced by an ever increasing insulating coating. Periodic cleaning of the heat exchanger is required, which is very time-consuming and costly for stubborn deposits.
  • cross-flow heat exchangers which consist of foils or thin strips and can be exchanged at high cost without great expense.
  • the inventor has therefore set himself the task of creating a heat exchanger of the type mentioned at the outset, which has a high degree of efficiency with less pressure loss, and which offers no problems in the edge region, more robust Has visible edges and is economical to manufacture.
  • the inflow cross sections are folded in at least on the inlet side of the media streams without changing the external dimensions of the heat exchanger, except for the flat outer areas, at least one adjacent surface element being clamped in the longitudinal fold of the inflow cross section formed.
  • the difference between the present invention and the known prior art is e.g. can be seen particularly well from FIG. 1 of FR, A, 2317617.
  • the inflow surfaces which are formed over their entire length (there designated by lamellae 10), oppose the media flow with great resistance, the bent edges are formed everywhere in a simple layer density and are therefore sensitive to mechanical impacts. According to the present application, however, the inflow surfaces, apart from the two outer areas, are folded in to form a longitudinal fold. Obviously, this means a multiple reinforcement against mechanical shocks and a significant reduction in flow resistance.
  • outflow cross-sections instead of inflow; folded;
  • the heat exchanger can therefore be used universally at low additional costs because the inlets and outlets can be interchanged.
  • This diffuser in- and spouts allow extremely low pressure losses because the media can flow in or out in a laminar manner.
  • heat exchangers can be assembled in parallel and / or in series to form larger, more powerful units.
  • heat exchangers assembled in series preferably only the inlet and possibly the outlet of the last element has a fold, while the inner surfaces lying against one another can remain unfolded.
  • the inflow cross-section preferably takes place on the inlet side or on the inlet and outlet side in such a way that the longitudinal fold comprises a flap folded inwards.
  • the inlets, together with the adjacent surface element, are reinforced at least five times. This minimizes the risk of damage during the transport and installation of heat exchangers.
  • the flow cross sections In the edge regions formed vertically to the surface elements, which are in no way cut out according to the present invention, the flow cross sections always remain unfolded.
  • the width of the unfolded inflow cross section corresponds at most to twice the spacing of the surface elements, and preferably the width of the unfolded inflow cross section corresponds approximately to the spacing of the surface elements. This width depends, among other things, on the thickness, hardness and the material of the surface elements used.
  • the edge running vertically to the surface elements must not be kinked or otherwise damaged when folded.
  • the spacers primarily perform a support function which prevents the surface elements from vibrating and bending at different pressures of the flow media.
  • the spacer further increases the exchange area.
  • the spacers are formed from the surface elements, for example as beads, nubs, warts or the like running in the flow direction.
  • the shaping can be carried out according to various methods known per se, for example by means of deep drawing.
  • the spacers are corrugated strips inserted into the flow channels and open in the flow direction.
  • the functions remain unchanged. All known cross sections of corrugated strips are suitable, for example sinusoidal, sawtooth-like, rectangular or trapezoidal.
  • the corrugated strips are preferably inserted in at least one longitudinal fold reducing the flow cross-section and clamped tightly there.
  • a fold with a flap folded inwards becomes at least six parts, the mechanical stability against damage is further improved.
  • the corrugated strips are expediently clamped on both sides.
  • the corrugated bands are preferably shortened compared to the surface elements or the outer dimensions of the heat exchanger.
  • the corrugated strips inserted into the heat exchanger do not extend to the folds, but are shortened, for example, by 1 to 3 cm on both sides, and extend essentially over the area of parallel surface elements.
  • the inserted corrugated strips can be formed in one piece, with continuous wave crests and wave troughs. This embodiment is particularly useful for heavily contaminated flow media.
  • the performance of the heat exchanger can be improved by staggering the wave crests and troughs one or more times. These dislocations can be varied both in number and in degree of dislocation. The greater the number of dislocations and the higher the degree of dislocation, the higher the performance for a given heat exchanger surface. On the other hand, however, because of the dislocations, the tendency for dirt deposits increases with performance. Depending on the degree of contamination of the flow media, a heat exchanger with appropriate corrugated tape is appropriate.
  • At least the inside of the fold can be filled with an adhesive or putty. This increases the tightness of the heat exchanger, its stability and the mechanical resistance of the edges. On the other hand, however, increased work and material costs have to be accepted, which can increase the production costs to a noticeable extent.
  • the outside of the inlaid fold can also be filled and coated with an adhesive or putty, which further enhances the advantages mentioned in the previous paragraph.
  • the surface elements and also the corrugated strips preferably consist of a 0.05-0.25 mm thick metal strip, for example strip steel, a hard aluminum alloy, brass or copper.
  • the metallic surface elements can be coated with a thin protective layer, which, however, conducts heat well and should have a low heat capacity.
  • the surface elements can for example painted or coated with an oxide layer in the case of aluminum.
  • flat elements and corrugated strips made of a plastic are also suitable, but because of the relatively low thermal conductivity, they are less suitable than the corresponding metallic components.
  • the heat exchanger is preferably designed for a maximum pressure difference of 1 m water column (10,000 Pa, 0.1 bar).
  • the heat exchanger 10 shown in FIG. 1 is arranged in an open housing with two lids 12 and four edge-covering angle profiles 14.
  • the U-shaped bent cover and the angle profiles 14 give the heat exchanger protection against deformation and mechanical damage and allow the heat exchanger to be fastened to a support and / or to connect the heat exchangers to one another in parallel or in series.
  • the actual heat exchanger 10 consists of stacked surface elements 16, which form the intermediate or partition walls. These surface elements consist in the present case of hard aluminum strips with a thickness of 0.1 mm, which are folded twice on two opposite sides and form a folded leg 16 '(Fig. 4). With regard to the stacking to form crosswise flow spaces, reference is also made to the already mentioned CH-A5 610 648.
  • Corrugated strips 18 are inserted between the surface elements 16, which support the surface elements 16 and improve the heat exchange.
  • the corrugated strips 18 are inserted alternately through 90 ° into the flow channels 34, 36.
  • air represented by an arrow can emit heat to air flowing in flow direction 22 represented by a further arrow when flowing in flow direction 20 through heat exchanger 10.
  • This cross-flow heat exchanger has large exchange surfaces, formed from the surface elements 16 and the corrugated strips 18.
  • the originally flat inflow cross sections in the visible region are compressed by folding into a longitudinal fold 24, as a result of which a diffuser inlet is formed. This does not change the outer dimensions of the heat exchanger.
  • Fig. 2 the longitudinal fold 24 is shown greatly enlarged.
  • the part of the surface element 16 which was originally folded and forms the flow cross-section 30 (FIG. 3) is designed as a flap 26 which is folded inwards.
  • An adjacent surface element 16 and a corrugated strip 18 are clamped between this tab and the outer parts of the surface element 16.
  • the longitudinal fold 24 formed in this way is designed as a sixfold layer, which means solid protection against mechanical damage.
  • the edge 18 shown in FIG. 3 and extending vertically to the surface elements 16 is essentially formed by the surface elements 16 stacked on top of one another once at right angles. These surfaces form the flow cross-sections 30, which can be seen partly from the front and partly in section.
  • the height of the inflow cross sections 30, corresponding to the distance between the surface elements 16, is denoted by a, the unfolded width of which is b. In the present example, a and b are approximately the same size.
  • the inlet between the longitudinal folds 24 has been significantly enlarged.
  • the surface element 16 rotated by 90 °, which likewise comprises a fold 24, is indicated by dotted lines.
  • FIG. 4 shows a further variant of a fold 24 with a flap 26 folded inwards.
  • the folded and folded surface element 16 is supported by a sawtooth-shaped corrugated strip 18 which is fastened in the fold 24 in a sealing manner by means of a cement compound.
  • An adjacent surface element 16N is inserted into the fold on the same side of the flap 26.
  • FIG. 2 differs in that it is trapezoidal in shape there and is not guided into the fold 24.
  • the hardening putty 32 is also inserted into the fold 24 from the outside. It has no sealing function, but forms an additional hardening and further improved protection of the fold 24 against external mechanical influences.
  • the corrugated strip 18 partially shown in FIG. 5 has lateral displacements which have a length L.
  • turbulence is increasingly generated on both sides of the corrugated strip 18 of a trapezoidal basic structure, which increases the efficiency of the heat exchanger.

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)
EP91810214A 1990-03-30 1991-03-25 Echangeur de chaleur, en particulier pour installation de ventilation Expired - Lifetime EP0449783B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH107290 1990-03-30
CH1072/90 1990-03-30

Publications (3)

Publication Number Publication Date
EP0449783A2 true EP0449783A2 (fr) 1991-10-02
EP0449783A3 EP0449783A3 (en) 1992-06-03
EP0449783B1 EP0449783B1 (fr) 1994-09-07

Family

ID=4201797

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91810214A Expired - Lifetime EP0449783B1 (fr) 1990-03-30 1991-03-25 Echangeur de chaleur, en particulier pour installation de ventilation

Country Status (3)

Country Link
EP (1) EP0449783B1 (fr)
AT (1) ATE111209T1 (fr)
DE (1) DE59102786D1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2689219A1 (fr) * 1992-03-30 1993-10-01 Carrier Sa Dispositif de réfrigération de fluide; son application au traitement de l'air; bac de production et de stockage de glace et faisceau tubulaire d'échange thermique propre à faire partie d'un tel dispositif.
FR2689622A1 (fr) * 1992-03-30 1993-10-08 Carrier Sa Faisceaux tubulaires d'échange thermique et bac de production et de stockage de glace comportant au moins un tel faisceau.
DE4237672A1 (de) * 1992-11-07 1994-05-11 Mtu Friedrichshafen Gmbh Wärmetauscher mit Flachrohren
DE4337634A1 (de) * 1993-11-04 1995-05-11 Funke Waerme Apparate Kg Plattenwärmeaustauscher
DE19530942A1 (de) * 1995-08-23 1997-02-27 Balcke Duerr Gmbh Plattenwärmetauscher
CH697104A5 (de) 2004-01-30 2008-04-30 Polybloc Ag Verfahren zum Kühlen eines Zuluftstroms für einen Raum.
WO2011148216A1 (fr) * 2010-05-26 2011-12-01 Mircea Dinulescu Échangeur de chaleur à plaques

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA3050503C (fr) 2019-07-24 2020-05-26 Inline Heat Recovery Inc. Unite de recuperation de chaleur

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR29315E (fr) * 1924-06-13 1925-07-24 C Ad Hubert Construction cellulaire constituée par des éléments amovibles, en forme de plaques, applicable aux échangeurs de chaleur
GB567642A (en) * 1942-10-05 1945-02-26 Harry Hitchen Improvements in or relating to heat exchange devices
FR2267533A1 (en) * 1974-04-11 1975-11-07 Meldem Charles Heat recoverer for ventilation system - has metal rectangular sheets forming chicane type air path
FR2311267A1 (fr) * 1975-05-14 1976-12-10 Interliz Anstalt Echangeur de chaleur a plaques a courants croises
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
FR2449261A1 (fr) * 1979-02-15 1980-09-12 Hoval Interliz Ag Echangeur de chaleur du type comportant un bloc echangeur a plaques
EP0054796A1 (fr) * 1980-12-19 1982-06-30 Raymond Godefroy Echangeur de chaleur modulaire à flux croisés et son procédé de fabrication
EP0062518A2 (fr) * 1981-04-03 1982-10-13 John Howard Coope Echangeurs de chaleur
EP0167993A2 (fr) * 1984-07-12 1986-01-15 Fischbach GmbH & Co.KG Verwaltungsgesellschaft Echangeur de chaleur construit à partir de plaques
DE3606253A1 (de) * 1985-05-01 1986-11-06 Showa Aluminum K.K., Sakai, Osaka Waermeaustauscher
US4681155A (en) * 1986-05-01 1987-07-21 The Garrett Corporation Lightweight, compact heat exchanger

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR29315E (fr) * 1924-06-13 1925-07-24 C Ad Hubert Construction cellulaire constituée par des éléments amovibles, en forme de plaques, applicable aux échangeurs de chaleur
GB567642A (en) * 1942-10-05 1945-02-26 Harry Hitchen Improvements in or relating to heat exchange devices
FR2267533A1 (en) * 1974-04-11 1975-11-07 Meldem Charles Heat recoverer for ventilation system - has metal rectangular sheets forming chicane type air path
FR2311267A1 (fr) * 1975-05-14 1976-12-10 Interliz Anstalt Echangeur de chaleur a plaques a courants croises
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
FR2449261A1 (fr) * 1979-02-15 1980-09-12 Hoval Interliz Ag Echangeur de chaleur du type comportant un bloc echangeur a plaques
EP0054796A1 (fr) * 1980-12-19 1982-06-30 Raymond Godefroy Echangeur de chaleur modulaire à flux croisés et son procédé de fabrication
EP0062518A2 (fr) * 1981-04-03 1982-10-13 John Howard Coope Echangeurs de chaleur
EP0167993A2 (fr) * 1984-07-12 1986-01-15 Fischbach GmbH & Co.KG Verwaltungsgesellschaft Echangeur de chaleur construit à partir de plaques
DE3606253A1 (de) * 1985-05-01 1986-11-06 Showa Aluminum K.K., Sakai, Osaka Waermeaustauscher
US4681155A (en) * 1986-05-01 1987-07-21 The Garrett Corporation Lightweight, compact heat exchanger

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2689219A1 (fr) * 1992-03-30 1993-10-01 Carrier Sa Dispositif de réfrigération de fluide; son application au traitement de l'air; bac de production et de stockage de glace et faisceau tubulaire d'échange thermique propre à faire partie d'un tel dispositif.
EP0564344A1 (fr) * 1992-03-30 1993-10-06 Carrier S.A. Dispositif de réfrigération de fluide; son application au traitement de l'air
EP0564342A1 (fr) * 1992-03-30 1993-10-06 Carrier S.A. Faisceaux tubulaires d'échange thermique et bac de production et de stockage de glace comportant au moins un tel faisceau
FR2689622A1 (fr) * 1992-03-30 1993-10-08 Carrier Sa Faisceaux tubulaires d'échange thermique et bac de production et de stockage de glace comportant au moins un tel faisceau.
US5369964A (en) * 1992-03-30 1994-12-06 Mauer; Georges Air conditioning apparatus
DE4237672A1 (de) * 1992-11-07 1994-05-11 Mtu Friedrichshafen Gmbh Wärmetauscher mit Flachrohren
DE4337634A1 (de) * 1993-11-04 1995-05-11 Funke Waerme Apparate Kg Plattenwärmeaustauscher
DE19530942A1 (de) * 1995-08-23 1997-02-27 Balcke Duerr Gmbh Plattenwärmetauscher
CH697104A5 (de) 2004-01-30 2008-04-30 Polybloc Ag Verfahren zum Kühlen eines Zuluftstroms für einen Raum.
WO2011148216A1 (fr) * 2010-05-26 2011-12-01 Mircea Dinulescu Échangeur de chaleur à plaques

Also Published As

Publication number Publication date
DE59102786D1 (de) 1994-10-13
EP0449783A3 (en) 1992-06-03
EP0449783B1 (fr) 1994-09-07
ATE111209T1 (de) 1994-09-15

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