EP0720720B1 - Channel heat exchanger - Google Patents

Abstract

A heat exchanger (1) for two flowing fluids (A, B) has parallel flow channels (4) whose cross-section is formed by layered and superimposed boards with a sinuous profile. Each board covers the flow channels (4) of the underlying board. Different fluids can flow through flow channels (4) located side by side. The inner angle theta of the open trapeziums formed by the sinuous profile has less than 90 DEG . Thanks to this small inner angle, each board lies on the underlying board and is prevented from intermeshing with it. This helps to increase stability at higher differential pressures and allows the weight of the heat exchanger to be reduced.

Description

The invention relates to a heat exchanger for, in particular two flowing fluids with parallel flow channels, the cross section of layers lying on top of each other Sheets with a meandering profile is formed, one the flow channels of the underlying one Covering the panel and being adjacent to each side Different fluids can flow through flow channels are.

Such a heat exchanger has become known from DD 243 088 A1.

For heat exchangers of standard series production such as plate heat exchangers or spiral heat exchangers often have sealing problems of the pressed plates or the Cover on the spiral heat exchanger, making it usable and the value in use is greatly reduced. Therefore at Plate heat exchangers with considerable effort a gluing, The plates are welded or soldered, however, this then results in mechanical cleaning of the flow cross sections is not possible or only possible to a limited extent.

Also the heat exchanger that became known from DD 243 088 Al is made up of individual ones in an S-shape Profile sheet metal strips built up, the profile of which is meandering Has cross section. The inside angle of the meandering Profile-formed open trapezoids are, however greater than 90 °, so that an overlying panel in the can intervene underneath and slide in. At higher pressure differences between the two heat exchange fluids there is an increased risk that the tables slipping into each other to an unwanted degree. In doing so the flow cross sections, flow velocities, effective Heat exchange surfaces and the static controllability of the overall structure in an uncontrolled manner.

However, the one known from DD 243 088 A1 increases Heat exchanger due to the sliding together of adjacent panels the number of heat exchangers for a given effective heat exchange surface required panels and thus the weight of the heat exchanger per room unit.

The invention is based on the object, one To further develop heat exchangers of the type mentioned in the introduction, that the superimposed panels no longer interlock slide, but that the boards without stabilizing Intermediate sheets can lie on top of each other and become one stable overall structure results, with economical use of materials a maximum heat exchange surface with thin sheets is achieved in a confined space.

This object is achieved in that the Inner angle of the open formed by the meandering profile Trapezoids are less than 90 °.

Due to the small internal angles according to the invention, there is a panel each on the adjacent table below so that an interlocking of adjacent panels just is prevented. This contributes to an increase in stability with larger pressure differences and leads to a weight reduction of the heat exchanger. The invention Heat exchanger is therefore a compact heat exchanger with a high specific heat exchange surface, for the most diverse Heat exchange tasks between gaseous and / or liquid Media as well as an evaporator, condenser and flow reactor applicable with exothermic and endothermic processes is. As a heat exchanger between gaseous media the heat exchanger can be used for waste heat, for example from exhaust air in buildings, factories and warehouses as well use in combination with extractor hoods. The heat exchanger can be used to preheat dry air in drying systems, for preheating combustion air such as in Bakeries, for drying processes or forced air cooling, for Condensation in tumble dryers for ventilation in livestock farming in stables and for heat exchange purposes in power plants and use exhaust gas treatment systems. For liquid media the heat exchanger can be used in car washes or in household appliances such as washing machines, dishwashers used will. Other areas of application are in air conditioning, in cooling processes such as control cabinet cooling or evaporative cooling, condensation, in evaporation technology such as as a film evaporator, in refrigeration systems, Continuous gas heaters and in boilers, forming stations for hot water and steam as well as in the automotive industry, for example for waste heat use and heating of the passenger compartment. Furthermore, the heat exchanger in the automotive industry due to its high compactness and small size can be used excellently for preheating wash water for windscreen and headlight washer systems and for charge air cooling in the turbocharger engine. The heat exchanger can be made of aluminum, steel, stainless steel, etc. Metals and alloys, or of plastics or Paper or other materials.

The inner angles of the meandering profile are preferred formed open trapezoids larger than 70 ° so that Relationship between material expenditure and heat exchange area of the flow channel is as optimal as possible and the ratio from heat transfer coefficient to weight or price of the heat exchanger is kept as large as possible.

Everyone is in a further advantageous development Plates of the heat exchanger from a single continuous Strips formed such that the flow channels of both Fluids are completely separated. The ongoing For example, profile strips run in a serpentine or S-shaped in or at right angles to the flow direction.

In a particularly preferred embodiment of the invention The walls of the flow channels are the heat exchanger roughened and / or with the flow of the flowing Structures influencing fluids. There with a channel flow, especially in larger dimensions smooth channels, the risk of deterioration in heat transfer through a laminar boundary layer of the flowing There is fluid on the walls, which leads to the invention roughened and / or structured duct wall as flow-specific baffles within the flow channel e.g. to create turbulence or spiral flows or double spiral flows, which increases the heat exchange between the fluids is increased or optimized.

It is very particularly preferred if always recurring Inflow processes within the flow channels can thereby be generated are that a Tefel in the direction of flow in certain Spaces in a short length in a flat Section, in particular with a turbulence-producing embossing, transforms.

In a further advantageous development, the fluid is into the individual flow channels via inclined surfaces and / or deflectable so that the fluids in selected flow channels for example a flow channel level or only one end half of the heat exchanger initiated can be. About the number of closed shut-off elements can also the residence time of the fluids in the Set the heat exchanger and thus the heat transfer coefficient and influence the flow direction of the fluids. Consequently hydraulic cleaning is also possible. Especially adjustable flaps can control the flow and heat exchange performance vary. These flaps can be driven or move magnets.

If in the area of the inlet and outlet openings of the flow channels Flow control elements are provided, via the the fluids can be introduced into the flow channels from the outside or are redirectable within the heat exchanger, so the inlet and outlet of each fluid at any angle lead into and out of the heat exchanger or within redirect the heat exchanger, the flow pressure losses be minimized.

Due to the acute-angled end face design, however even without these flow guide elements, the introduction or discharge of the fluid on the front and also on the side, i.e. at 90 ° Realize angles. According to the invention, these are in the housing and at the front, V-shaped sealing element openings Seals and filters are provided.

A flow distributor and a are particularly preferred Flow combiner for a fluid as one in the flow direction over the entire cross-section of the flow level (s) extending flat channel section without flow channels trained and the flow channels of the other Fluids in this (n) flow plane (s) at their respective Ends, especially with an inclined surface, closed are. Then it flows into the heat exchanger e.g. about its total cross-sectional area introduced fluid into all open Flow channels without entering the flow channels of the other fluids. So one can only have an opening cross-section fluid flowing into the heat exchanger to all desired flow channels in the heat exchanger into one Checkerboard-like flow cross-section can be distributed and so with low flow pressure loss, since none 90 ° deflection, maximum heat exchange can be achieved.

According to the invention, this is the profile forming the flow channels compressed into a plane at its respective ends. Profile sheets manufactured using the deep-drawing process with an acute-angled trapezoidal shape Cross section can be easily compressed, so that with a meandering basic profile also structures closing certain flow channels easy to manufacture.

It is particularly advantageous if two neighboring, profiles compressed from each into a plane respective level to a closing the flow level End wall can be bent.

If the channel sections are each only open to a fluid Have front half and this entry and exit side Face halves of a fluid preferably diagonally opposite in the direction of flow, so the Flows through the heat exchanger according to the invention diagonally and with respect a flow short-circuit of the heat exchanger is prevented. In addition, this aerodynamically favorable, almost straight flow compared to the pressure drop known counterflow designs reduced.

Those forming the flow channels are particularly preferred Panels can be arranged in a housing, which can preferably also be dismantled, what the assembly and disassembly as well as the Cleaning of the individual parts forming the heat exchanger facilitated. When using a removable face The heat exchanger package is also a V-shaped sealing element easily removable from a one-piece housing.

Several side heat exchangers are very particularly preferred and / or in the form of a modular system and / or corner can be coupled to one another, so that adaptations to predetermined geometries, e.g. Volume flows and heat exchange performance possible are.

A fin heat exchanger also falls within the scope of the invention, in which a fluid, e.g. Air, parallel flow channels with rectangular profile, trapezoidal profile or excessive trapezoidal profile or similar parts of profile pieces. Of the Heat exchange with another fluid, e.g. with a liquid, done by flowing the liquid through pipes etc. through the finned heat exchanger or on its outer surfaces is led along.

Further advantages result from the description and the attached drawing. Likewise, the above and the features listed further according to the invention each individually or in any order can be used together. The mentioned embodiments are not to be understood as a final list, rather, they have an exemplary character.

Fig. 1a

schematisch den Querschnitt des erfindungsgemäßen Wärmetauschers mit parallelen, spitzwinkligtrapezförmigen Strömungskanälen, umgeben von einem Gehäuse;

Fig. 1b

schematisch die Verteilung zweier Fluide A und B in den Strömungskanälen der Fig. 1a, sowie den angedeuteten zwei-dimensionalen Wärmetransport;

Fig. 2a

in perspektivischer Ansicht die Strömungskanäle der Fig. 1b mit zwei im Gegenstromverfahren durchströmenden Fluiden A und B;

Fign. 2b-e

in einer der Fig. 2a entsprechender Ansicht die Strömungskanäle des Wärmetauschers jeweils mit in Durchströmrichtung verschieden strukturierten Kanalwandungen;

Fig. 3a

zwei Strömungsebenen zweier Fluide in Explosionsdarstellung mit für das andere Fluid verschlossenen Strömungsteilern;

Fig. 3b

den Strömungsverlauf der beiden Fluide entlang der Ebene IIIb-IIIb der Fig. 3a;

Fig. 3c

den aus dem spitzwinkligen Trapezprofil erzeugten quasi-ebenen Einströmbereich entlang der Ebene IIIc-III3c der Fig. 3a;

Fig. 4

in perspektivischer Ansicht Strömungskanäle mit zwei im Gegenstrom und in abwechselnde Strömungsebenen eingeleiteten Fluiden;

Fig.

5 in perspektivischer Ansicht Strömungskanäle mit unterbrochenen Strömungskanälen und seitlicher Ausleitung eines Fluids;

Fign. 6a,b

in perspektivischer Ansicht einen Wärmetauscher mit die äußeren Strömungskanäle seitlich teilweise abschließenden Seitenwänden und mit seitlicher Einleitung eines Fluids;

Fig. 6c

schematisch die Ein- und Ausflußrichtungen der beiden Fluide gemäß den Fign. 6a und b;

Fign. 7a-d

einen Wärmetauscher mit zerlegbarem Gehäuse und mit V-förmigen Stirnseiten des Wärmetauscherpakets sowie die Durchströmrichtungen der Fluide und desweiteren ein flexibles Verbindungselement;

Fig. 8

einen Wärmetauscher mit zerlegbarem Gehäuse, mit rechtwinkligen Stirnseiten des Wärmetauscherpakets und mit seitlichen Öffnungen;

Fig. 9

einen analog zu dem der Fig. 7a gestalteten Wärmetauscher in einem einteiligen Gehäuse;

Fig. 10

in perspektivischer Teilansicht Strömungskanäle eines Rippen-Wärmetauschers mit rechtwinklig zur Luft-Durchströmrichtung hindurchtretenden Rohren runden Querschnitts;

Fig. 11

die Strömungskanäle der Fig. 27 mit Rohren länglichen Querschnitts.

Fig. 12

einen Rippenwärmetauscher für zwei in verschiedenen Ebenen getrennt und rechtwinklig zueinander strömende Fluide; und

Fig. 13a-c

verschiedene mögliche Profilformen des Strömungskanalquerschnitts für Wärmetauscher, Raumheizkörper und Rippenwärmetauscher.

The invention is illustrated in the drawing and is explained in more detail using exemplary embodiments. Show it:

Fig. 1a

schematically the cross section of the heat exchanger according to the invention with parallel, acute-angled trapezoidal flow channels, surrounded by a housing;

Fig. 1b

schematically the distribution of two fluids A and B in the flow channels of Figure 1a, as well as the indicated two-dimensional heat transfer;

Fig. 2a

a perspective view of the flow channels of Figure 1b with two fluids A and B flowing in the countercurrent process.

Fig. 2b-e

in a view corresponding to FIG. 2a, the flow channels of the heat exchanger each with channel walls structured differently in the flow direction;

Fig. 3a

two flow planes of two fluids in an exploded view with flow dividers closed for the other fluid;

Fig. 3b

the flow of the two fluids along the plane IIIb-IIIb of Fig. 3a;

Fig. 3c

the quasi-flat inflow region generated from the acute-angled trapezoidal profile along the plane IIIc-III3c of FIG. 3a;

Fig. 4

in perspective view flow channels with two fluids introduced in countercurrent and in alternating flow levels;

Fig.

5 a perspective view of flow channels with interrupted flow channels and lateral discharge of a fluid;

Fig. 6a, b

a perspective view of a heat exchanger with the outer flow channels laterally partially closing side walls and with the lateral introduction of a fluid;

Fig. 6c

schematically the inflow and outflow directions of the two fluids according to FIGS. 6a and b;

Fig. 7a-d

a heat exchanger with a housing that can be dismantled and with V-shaped end faces of the heat exchanger package and the flow directions of the fluids and also a flexible connecting element;

Fig. 8

a heat exchanger with a housing that can be dismantled, with right-angled faces of the heat exchanger package and with side openings;

Fig. 9

an analogous to that of Figure 7a designed heat exchanger in a one-piece housing.

Fig. 10

in partial perspective view flow channels of a finned heat exchanger with tubes of round cross-section passing at right angles to the air flow direction;

Fig. 11

the flow channels of Fig. 27 with tubes of elongated cross section.

Fig. 12

a finned heat exchanger for two fluids separated in different planes and flowing at right angles to each other; and

13a-c

Different possible profile shapes of the flow channel cross section for heat exchangers, space heaters and fin heat exchangers.

The heat exchanger designated by 1 in FIG. 1a has a housing 2, in which by means of a continuous sheet metal strip 3 flow channels 4 for two fluids, for example A, B are formed. Inscribed in the drawing a filled arrow the fluid A, an unfilled Arrow the fluid B. The metal strip 3 has a meandering shape Profile whose open inside angle  is less than Are 90 °. Inside the housing 2 is the meandering Sheet metal strip 3 itself arranged in a serpentine or S-shape, that parallel flow channel planes are formed. The sheet profile lies on a flow level the underlying sheet metal profile, as shown schematically at 5 is indicated. The two longitudinal edges 6a, b of the Sheet metal strip 3 are either with each other or with the housing 2 connected leakage-free, so that laterally adjacent Flow channels 4 each completely from a different fluid and flows hermetically separated from one another by sheet metal will. As shown in Fig. 1b, mixing takes place of the fluids flowing through the flow channels 4 A, B does not take place. Due to the almost square structure of the Flow channels 4 are used for heat exchange between the two Fluids A, B each on four sides of a channel 4, such as it is indicated by the double arrows 7. The heat exchange surface can only be compared to one of parallel Double plates of existing heat exchangers.

To further increase the heat exchange, flow through the two fluids A, B according to FIG. 2a, the flow channels 4 in opposite flow direction. With a channel flow, especially in larger flow channels with smooth walls, as shown in Fig. 2a the risk of deterioration in heat transfer between the two fluids A, B through the training each a laminar boundary layer of the flowing fluid the smooth wall. The figures 2b to e show across and formed obliquely to the flow direction of the flow channels 4 Flow baffles in the form of furrows 8a to 8d, over which the flow behavior of the flowing Influences fluids. So they lead to at right angles Flow direction of the fluids running furrows 8a, d Turbulence, while those running at an angle to the flow direction Furrows 8b for a simple spiral flow 8b 'and the V-shaped or herringbone-like furrows 8c lead to a double spiral flow 8c '. This structured Channel walls prevent a laminar boundary layer and improve the heat exchange between the two fluids A, B.

3a shows an exploded view of the otherwise superimposed ones Profile sheets. The illustration shows how the profile of the quasi-flat flat plates (see Fig. 3c) merges into the meandering profile structure, the Transition e.g. from level 9 to the "trapezoidal roof" 10 over the oblique discharge surfaces 10a; analogously, the Transition to the "Trapez Valley". The flow course in this Transition area (channel distributor) is from the sectional view 3b can be seen, it being clearly recognizable that the entry of the medium A from a flat, flat Gap (first flow level) in the channels of two flow levels (Partial streams A 'and A "according to FIG. 4), whereby the checkerboard-like flow profile well shown in FIG. 4 arises. Entry and exit sides of the flow channels are the elevations 10 with an end surface, in the exemplary embodiment with a curved inflow surface 10a completed the entry of the other fluid in the flow direction to prevent. In this way, the increase heat exchange achievable with smooth heat exchangers. As Fig. 3b shows, the elevations 10 Fluid flows A, B in two partial flows A ', A "and B', B "divided and parallel to each other in the flow channel between or performed on the surveys 10.

The flow channels 4 shown in FIG. 4 differ from those of FIG. 1a in that on the outside diagonally adjacent flow channels 4a, b of a fluid are connected to one another via openings 11. This is shown in the rear view of FIG. 4 for the outer flow channels 4a, b. The front part of Fig. 4 shows the separate inflow of the two fluids A, B in adjacent flow levels in the countercurrent process. As shown in Figs. 3a and b, the introduction of a fluid into the flow channels 4a, 4b is achieved in that elevations 10 are provided with closed inclined surfaces 10a. The fluid flow A is split up via the inclined surface 10a into a first partial flow A 'and a second partial flow A ". In the flow plane open for one fluid, the cross sections of the flow channels of the other fluid are completely closed off via inclined surfaces 12. In this way, the two Fluids A, B are introduced separately from one another into flow planes 4 _A , 4 _B that are open to them and are distributed into the intended flow channels of the respective fluid.

Because the heat exchange in the laminar area occurs during the inflow phase increased, is a flow interrupted again and again advantageous. This can be caused by recurring start-up processes in the flow channel 4 or, as shown in FIG. 5, in a flow level can be achieved in that in certain Distances the flow channels 4 on a short Length in a flat channel 13 between two inclined surfaces 12a, b as in a plate heat exchanger and from there the flow is redistributed into the flow channels 4 becomes. Fig. 5 also shows that the two in countercurrent fluids A, B flowing through the flow channels 4 either on the front (Fluid A) or from the side (Fluid B) can be introduced into different flow levels. Through all flow channels 4 one flow level ahead common channel section 14 are all flow channels 4 of a fluid in this flow plane with each other connected. That introduced into this flow plane Fluid is distributed evenly across the individual flow channels 4th

The lateral sealing of the flow channels open to the outside 4 takes place either through a smooth side wall 15a or by profiling according to the flow levels Sidewall 15b (Fig. 6a). The introduction of the fluids A, B in This embodiment is carried out through side openings 16 in the side walls 15a, b. Because the flow planes of the other Fluids with an S-shaped overlay of the sheet metal strip resulting from the bending edge closed the fluid can be open over the entire Cross section 16 of the side walls 15 are fed. The derivative the fluid takes place according to FIG. 6a via the end face of the flow channels 4, so that the introduction and discharge of the both fluids A, B are each perpendicular to each other. In the case of an overlapping S-shape in the direction of flow Profile sheet strips, as shown in Fig. 6b, are the profiled side parts 15b with corresponding recesses Mistake. Fig. 6c again illustrates each Entry and exit directions running at right angles to one another the fluids A, B in the heat exchanger 1.

7a shows a heat exchanger 101 which can be dismantled and which consists of two housing halves 102a, b which can be connected to one another, a profiled sheet 103 which forms flow channels 104 and a cover 117 with flow deflection elements 117a. At their entry and exit ends, the identically designed housing halves 102a, b have two preferably square openings 118a, b and two side openings 119a, b, into which the covers 117 (with and without flow control elements 117a) can be inserted. The housing 102, 602, the cover 117, 617, the gap 627 and the connecting rib 6 are preferably made of plastic and can be connected to one another in a detachable and simple manner. The end faces 103 'of the profiled sheet 103 are V-shaped and, when the two housing halves 102a, b are connected, are in a form-fitting manner against likewise V-shaped stops 102' within the respective housing half 102a, b, a seal preferably being inserted for sealing purposes, which is adapted to the sealing surface 102. The flow directing elements 117a consist of parallel baffles 117a 'spaced apart from one another and one or two cover surface (s) 117b. Preferably, both the end angle β of the V-shaped end face of the profiled plate 103 and the deflection angle of the flow deflecting elements 117 are 45 °, so that the fluids between the guide plates 117a can be introduced or discharged parallel to the flow direction via the end sides of the heat exchanger 101, as in the fig. 7a, b is shown. If the covers with flow guide elements 117a are inserted into the front openings, the laterally entering fluids A, B can also be introduced into the heat exchanger 101 parallel to the flow direction. FIG. 7c shows the flow planes 4 _A , 4 _B which are each open for a fluid and closed by end strips, which correspond to those of FIG. 4 with the exception of the V-shaped end face. The two housing halves 102a, b can be easily connected or detached to one another by means of fastening means in the form of locking brackets 121 which engage with projections 120 on the heat exchanger 101. The covers 117 can also be easily attached or detached using a similar locking mechanism between projections 117c on the covers 117 and locking brackets 121 '. 7d shows the longitudinal section of the assembled heat exchanger 101, a flexible intermediate piece 121 being installed here for improved expansion absorption and assembly. This adapter can also be attached to the end of the heat exchanger.

8 is another embodiment of a heat exchanger 201 shown, in which the one-piece housing halves in FIG. 7a 102a, b in turn through two housing quarters 202a ', a ", b', b" are formed. The individual housing quarters 202 and the front cover 222 and die die side covers 223 covering side openings 219 are attached with locking brackets 221, which in turn with Projections 220 and 217c on the housing quarters 202a, b and cooperate on the end parts 217c. The one assembled State of the heat exchanger 201 to the heat exchanger package pressed housing parts are each with sealant 224 sealed. The profiled sheet 203 is on the ends of rectangular end faces 203 '. The front Covers 222 with protrusions 217c are made by means of Seal 224 and clamping means tightly connected to the housing.

FIG. 9 shows a heat exchanger designed analogously to FIG. 7a 103 in a housing 602, which, however, in one piece is. The exploded view shows that the housing 602 consists of a continuous, rectangular channel 602, which is easy to produce as a drawn part. The seal on the V-shaped end face 103 'takes place via a removable V-shaped sealing element 623, the front and side preferably square and identically shaped openings 618 ', the inflow and outflow both at the end as well as sideways. The locking of the V-shaped Sealing elements in the housing are made by inserting them a cover 617 or other connecting element 626, 627 through the side housing opening 619 into the lateral opening 619 'of the V-shaped sealing element 623 into where the plug-in element snaps away. To this Way is in the component system with simple means a maintenance-friendly, multivalent use of the heat exchanger possible.

Between the sealing surface 602 'of the V-shaped sealing element 623 and the V-shaped end face 103 'of the heat exchanger an 8-shaped frame seal 624 is provided for sealing. This seal 624 can 625 over the entire surface be so that an incoming medium is filtered at the same time becomes.

To two different modes of action (sealing and filtering) To be able to realize with one material becomes this material 624, 625 on the active sealing surface on the surface and / or treated in such a way that impermeability for the flowing medium and thus a good sealing effect is achieved.

The connection between housings (modular form) and between Housing with V-shaped connecting element 625 and connecting elements (such as connecting nipples, flexible connecting elements 651, elbows 626, transition pieces 627 from round to square-symmetrical or asymmetrical), Ventilation grilles at the openings, condensate discharge elements, Blanket (617 etc.) is preferably a removable Snap connection realized, preferably from Plug part 628 and receptacle (socket) part 628 'there.

The figures 10 and 11 show a fin heat exchanger 701, where the ribs are turned back and forth and a rectangle-like Own profile structure. When turning back and forth and thus when the profiled sheet metal strip is superimposed 703 creates a chessboard-like structure very high heat exchange area per room unit. The flow channels 704 are made of a, in particular gaseous, fluid A flows through like air, the heat exchange with a in particular liquid fluid B takes place in pipes 705, 705 'perpendicular to the flow channels 704 the profiled sheet 703 flows through. The tubes 705, 705 'have either a round (Fig. 10) or an elongated cross section (Fig. 11).

The advantages of the finned heat exchanger 701 can be seen in that the heat transfer is intensified on the air side. This is due to the fact that with liquid-air heat exchangers on the Air side due to media only a significantly lower heat transfer is possible, the heat exchange surface on the Air side (heat exchange fins) are designed so that on The largest possible heat exchange surface accommodated in a confined space is, which in the best case at the same time in itself should be structured to match the heat transfer coefficient on the Increase air side. This goal can be achieved with the profiled Generate metal strips 703, with its profile shape no parallel ribs are created, but by the and turning and stacking a checkerboard-like Structure arises. Through additional structuring the channel wall is corrugated or structured differently, so Turbulence or spiral flows arise. Through the Rib profiling is the one actively involved in the heat exchange Rib area increased by approx. 60%. It can be used for the same outer dimensions of a finned heat exchanger the heat exchange surface and thus the compactness and heat exchange performance be increased significantly, or while maintaining one required heat exchange surface is the entire fin heat exchanger in its outer dimensions much smaller.

In Fig. 12 is another embodiment of a fin heat exchanger 701 'shown by two gaseous fluids A, B at right angles and in separate flow channels is flowed through. Due to the large profile surface of the Fluid A the heat exchange with the fluid B can also be increased here.

As the fig. 13a to 13c show the rib profile Rectangular profile, a trapezoidal profile, an elevated trapezoidal profile, the trapezoidal cones are acute-angled, or the like Profiles.

Claims (13)

1. Heat exchanger (1), especially for two through-running fluids (A, B) with parallel channels (4), which cross-sectionally consists of meander-like profile sheets arranged in layers, whereas the sheet respectively located above covers the channels (4) of the sheet respectively located below, and whereas laterally neighboured channels (4) can be flown through by different fluids, characterized by the fact that the interior angles  of the open trapezoids formed by the meander profile are smaller than 90 °.
2. Heat exchanger as described under 1., characterized by the fact that the interior angles  are greater than 70 °.
3. Heat exchanger as described under 1. or 2., characterized by the fact that all sheets (1) of the heat exchanger are designed as one continuous strip (3) in such a way that the channels (4) for both fluids (A, B) are completely separated from each other.
4. Heat exchanger as described under one of the previous items, characterized by the fact that the walls of the channels (4) are roughened and/or have structured patterns (8a, 8b, 8c, 8d) which influence the flow of the through-running fluids.
5. Heat exchanger as described under one of the previous items, characterized by the fact that constantly recurring flowing processes inside the channels (4) can be generated by means of a method in which one sheet moves into a flat section (13) in the direction of flow over a short distance in certain intervals, especially with a shape that generates turbulences.
6. Heat exchanger as described under one of the previous items, characterized by the fact that a fluid can be led into or out of the individual channels (4) via inclined planes (12a, b).
7. Heat exchanger as described under one of the previous items, characterized by the fact that flow guide elements (117a) are installed in the area of the channel inlet and outlet openings of the channels (4). By means of these flow guide elements the fluids (A, B) can be led into the channels (4) from outside, or by-passed inside the heat exchanger (101).
8. Heat exchanger as described under one of the previous items, characterized by the fact that a flow distributor together with a flow collector form a plane channel section (14; 114) without channels covering the complete cross-section of the flow level(s) in the direction of flow for one fluid, and that the channels (4; 104) of the other fluid at this/these flow level(s) are locked at their respective ends by means of an inclined plane (12a).
9. Heat exchanger as described under one of the previous items, characterized by the fact that the profile forming the channels (4) is pressed together at its ends on one level (9).
10. Heat exchanger as described under 9., characterized by the fact that two neighboured profiles which are pressed together on one level each can be bent from their respective levels to an end wall (16b) which locks the flow level.
11. Heat exchanger as described under 8., characterized by the fact that the channel sections (114) only have one preferably V-shaped half of a end wall (113') each which is open for one fluid, and that these halves of end walls (113') located on the inlet and outlet respectively are positioned diagonally opposite to each other in the direction of flow.
12. Heat exchanger as described under one of the previous items, characterized by the fact that the sheets forming the channels (4) can be arranged inside a housing (2; 102; 602) that is preferably dismountable.
13. A set of heat exchanger modules as described under one of the previous items 1, to 12, characterized by the fact that several heat exchangers can be coupled with each other either next to each other and/or in fine and/or cornerwise.

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