DE19519511A1 - Heat exchanger using hollow plate - Google Patents

Abstract

The heat exchanger has two heat transfer surfaces with flow and counterflow channels between them, formed by a hollow plate (12). The hollow plate is composed of extruded or forged hollow profile plates of plastics or metal, having separating webs (32) which bound several of the flow channels (16) between the wide-side walls (18). The hollow profile plates may be mfd. by extrusion. The material used may be polypropylene, polyethylene, polyvinyl chloride, polystyrene or acrylonitrile butadiene styrene, or aluminium or an aluminium alloy. There may be spacers between the wide side walls, bounding at least sectors of the counterflow channels (20).

Description

The invention relates to a heat exchanger for two or several, preferably gaseous media of different Temperature, with two by heat transfer surfaces of one other separate, from the two media via respective inputs and outlet openings flow through according to the counterflow principle ren groups of flow channels, several at a distance from stacked, with their broad sides walls forming the heat transfer surfaces, from each other of the parallel flow channels of one medium th hollow plates, Ge running between the hollow plates flow channels of the other medium and two on opposite arranged sides of the stack of hollow plates, edge open on one side and at mouth openings in the flow chamber channels or counterflow channels opening groups of plate white se separate deflection chambers that over the Mün openings of one of the media with flow deflection are flowable. The invention further relates to various the types of use of the heat exchanger.

Heat exchangers of the type mentioned have long been part of State of the art. They enable targeted heat transfer bearing in the direction of a temperature gradient between two or more fluid material or media flows and serve ins special of the recovery of waste heat. The heat transfer In so-called recuperators, supply occurs indirectly as a result Heat transfer through a fixed partition, along which the media separately from each other in opposite directions flow in the set direction. Because of the counterflow approaches the outlet temperature of the heat emitting Inlet temperature of the heat-absorbing medium. For the  heat occurring through the partition transport is approximate

Q = k A ΔT _m , (1)

with k as the heat transfer coefficient, A as the total transfer area touched by the media and ΔT _m as the mean temperature difference between the media. The processes relevant to heat transfer are reflected in the k value, which depends on the heat transfer between the flowing medium and the partition on both sides of the same and on the heat conduction in the partition. The efficiency achieved in the heat transfer performance, ie the ratio of the recovered energy to the maximum recoverable energy, can be simplified by the number of heat losses or the temperature efficiency

η = (T₂ - T₁) / (T₃ - T₁) (2)

are shown, T₁ and T₂ the entry and exit temperatures of the colder and T₃ the inlet temperature of the mean warmer medium. In countercurrent, they are in ge given temperature difference achievable efficiencies on largest compared to those at other flow Leading such as direct current, cross current or cross counter current. In In practice, countercurrent heat exchangers are effective achieved from 70 to 95%, while cross-flow heat exchanger significantly lower, in the range of 50 to 70 % lying efficiency. Countercurrent heat exchange However, shearers generally have a complicated design. The most common countercurrent heat exchangers exist as a so-called tube bundle exchanger from a jacket and a tube bundle held therein by a tube sheet as well as connecting pieces for the supply and discharge of the tube and fluid on the jacket side. Such constructions point  require a lot of space, are expensive to manufacture and cause difficulties in mass production. They therefore come especially for use in climatic technology systems where, in addition to efficiency, the purchase price and the size important evaluation factors are hardly out of the question.

Compact designs with comparatively cheap heat outputs Exchange area can be replaced by so-called plate exchangers to reach. With these it is known per se, thin, grooved to arrange te or corrugated plates in a stack and that warmer and colder medium alternating between the the spaces formed between the plates. To the material separation of the heat-exchanging media one and on the outlet side, when plates are replaced the edge openings of the gaps shear media-wise separates two opposite ends closed and the external channel strips at the respective lead connected open end faces. Inevitably he with this connection principle there is a cross current flow, with the mentioned disadvantage of lower efficiency.

With a heat exchanger of the type mentioned (DE-A-27 06 253) the one media stream is U-shaped or Z-shaped using trapezoidal or diamond-shaped intermediate layers led out while the other media flow through plates shaped hollow body with rectilinear, parallel flow chamber is led out. The Zwi forming the counterflow channels creases are arranged parallel to each other te webs that limit the available heat transfer area reduce che. The known heat exchanger consists of ceramic materials, especially for high temperature applications are determined. An application for indoor air conditioning tion, especially using evaporative coolers, is not provided there and because of the relatively small heat  The passage coefficients are also not useful.

Proceeding from this, the invention is based on the object to ent ent a heat exchanger of the type specified winding, based on countercurrent flow at high efficiency enables economical production and a compact design with a large heat transfer area and opens up new applications.

To solve this problem, the in claims 1, 12th and 18 specified combinations of features proposed. Before partial configurations, further training and uses the invention result from the dependent claims.

The invention is based on the idea that an effective and uniform heat transfer can be achieved can that the hollow plates thin-walled broad side walls and parallel partition arranged between the broad side walls have webs that are parallel to each other Limit open flow channels on the face. To a host to ensure the economic production of such hollow panels most, is proposed according to a first alternative of the invention suggest that the hollow sheets as extruded or extruded pressed out hollow profile sheets made of plastic or metal forms, which be a variety of the flow channels bordering, molded between their broad side walls, have mutually parallel dividers. With this measure mass production at low cost is possible Lich. The profile shapes of the hollow profile plates, in particular the thickness of the side walls, the profile shape of the dividers and The channels and their length can meet the respective requirements can be adapted easily and optimally. Dependent the application and temperature range of the heat exchanger the hollow profile panels made of plastics from the Po lypropylene, polyethylene, polyvinyl chloride, polystyrene, ABS  extruded or from metals of the group aluminum, alumi nium alloys are extruded. When using this Materials it is possible to be extremely thin-walled and yet to produce dimensionally stable hollow profile plates, in particular their good heat transfer properties, low weight and low costs associated with material savings can be worn.

According to a preferred embodiment of the invention, a Two-stream system in a particularly simple way through between the spacer arranged spacers who realized the one that the counterflow channels at least in sections limit. The spacers can be in the form of strips cuts from the same hollow profile material as for the Be Limitation of the flow channels provided hollow profile plates exist that are parallel to each other at equal intervals the hollow profile plates are arranged and their dividers run parallel to the dividers of the hollow profile panels. This ensures sufficient dimensional stability, while at the same time the thickness of the heat transfer surfaces between the media essentially on the wall thickness of the Broad side walls of the hollow profile plates remain limited. Thereby the heat transfer coefficient k (equation 1) and increases the heat transfer performance.

The strip-shaped ones advantageously extend Hollow profile plate sections with their transverse or oblique their dividers running longitudinal edges over the entire Height or width of the hollow profile panels and limit the Deflection chambers on the mouth side to the counterflow channels there. As a result, it is passed through the deflection chambers led media stream split into individual streams, and into uniformly from between the hollow profile plates Formed counterflow channels supplied or from these like the dissipated. The hollow profile plate sections serve too  equal to as current disturbance elements that the laminar boundary layer the media flow and thereby destroy the heat exchange improve.

An advantageous embodiment of the invention provides that the spacers from corrugated profiled plates Plastic or metal, which together with the neighboring beard wide side walls of the hollow profile panels a variety ver parallel to the dividers of the hollow section plates limit current flow channels. Deviating from this the spacers can also consist of several in flow direction at a distance from each other between the two facing broad side walls of the hollow section plates th, wavy profiled plate strips consist of together with the neighboring broad side walls Chen parallel to the dividers of the hollow profile panels form running channel sections. The wavy profiling th plate strips expediently extend with ih Ren extending transversely or obliquely to the channel sections Longitudinal edges over the entire height or width of the Hohlpro film plates and limit the deflection chambers at the mouth side to the counterflow channels.

It is also possible that the spacers from the Molded plates, ver parallel to the flow channels running guide ribs exist. The guide ribs can with same longitudinal offset to each other across the width of the hollow plates spaced from each other and with their Face the mouth openings of the deflection chambers Zen.

According to a second alternative of the invention, the Hollow plates each consisting of a flat base plate and one a broad zigzag or wavy profile parallel contact lines with the base plate un  ter formation of the flow channels or counterflow channels bound profile plate formed. Preferably the base plate and the profile plate as a one-piece extrusion or extruded part made of plastic or metal. But it is also possible the base plate and the profile plate as separate molded parts made of plastic or metal train that glued together at their contact lines or are welded. For sealing along the edge a hollow plate is the preferably rectangular base plate te on their side edges preferably to the side of the profile plate bent by about 90 °, the bent edges that of the base plate one of the maximum profile depth of the Pro filplatte have appropriate width and in the area of Inlet and outlet openings can be interrupted.

According to a third alternative of the invention, the hollow plates each consist of a flat base plate and a large number protrude from over a broad side surface of the base plate the, with lateral limitation of the current or counter current channels ge parallel to each other forms, which are integrally connected to the base plate can. The base plate and the guide are advantageous rip out as a one-piece extrusion or extrusion Made of plastic or metal.

According to a preferred embodiment of the invention Deflection chambers in groups, each with an on or off let opening to opposite, parallel to the flow channels running end faces of the plate stack towards the edge open on both sides and with right-angled deflection of the media flow through. This makes it possible for the media for flow threads that are separated from each other to different ones Lead end faces of the plate stack, on which external Pipes, in particular manholes for ventilation systems can be easily connected separately  are. By redirecting the media flows, the Flow or counterflow channels are independent in length from the cross sections of the inlet and outlet openings be.

The deflection chambers are advantageously wedge-shaped in outline mig trained and extend with two to the one or outlet opening adjacent, an acute angle closing narrow-side boundary surfaces over the ge entire width of the hollow panels. The wedge shape makes one uniform flow distribution or a constant Pressure drop across all orifices and thus one uniform heat transfer in all channel strips enough. This will in particular be uneven temperature profiles, as they are due to known plate exchangers cross-flow over the flow cross-section avoided.

Advantageously, the deflection chambers open at one of them Narrow-sided boundary surfaces in the mouth openings of the flow channels or counterflow channels and are at their other narrow-sided boundary surface by a forehead wall sealed gas-tight. This will focus on one achieved a diversion of the media flow without that further precautions such as attachment of baffles are required.

Around the two media on the opposite forehead th of the plate stack in and out, the Counterflow channels on the inflow and outflow sides in one of the two groups of deflection chambers open and the flow chamber channels at inlet and outlet openings on opposite End faces of the stack of hollow plates or vice versa. Alternatively, the media can be juxtaposed Adjacent end faces of the plate stack to and from  be discharged when the flow channels on the input side and the counterflow channels on the output side with one of the groups pen are connected by deflection chambers, or vice versa.

Another preferred embodiment of the invention provides before that the flow channels and the counterflow channels aisle and outlet side with one of the groups of Um Steering chambers are connected and that the inlet and outlet the stacked hollow panels at both ends of the pile alternately towards the opposite Point along the long sides of the hollow panels. This gives you one two mutually parallel inlet openings and Outlet openings for the two media flows.

An advantageous modification of this design provides that the flow channels on the input side and on the output side one of the groups of deflection chambers are connected that the Counterflow channels only on the input or output side with one of the Groups of deflection chambers are connected and that the inlet and outlet openings of the sandwich-like stack th hollow plates at one end of the stack alternately after opposite have opposite longitudinal sides of the hollow plates.

According to a further advantageous embodiment of the Erfin are in the flow channels and / or counterflow channels arranged flow obstacles to generate a turbu lenten flow arranged. This is the heat exchange further improved between the media.

For use in evaporative coolers, it is advantageous if the flow channels and the counterflow channels of a hollow profile plate pair or stack in the area of their one, facing mouth openings to form a closed flow reversal chamber communicate with each other Ren. In the flow reversal chamber water spray nozzles  and a water reservoir through which the medium can flow be ordered, the water reservoir made of a textile Fiber fabric or nonwoven fabric can exist.

A preferred use of the heat according to the invention tauschers sees its use in air conditioning systems for heating or cooling a supplied outside air flow using the heat content of an exhaust air flow in front. With such applications, there are no extreme requirements the pressure and temperature resistance of the heat exchanger posed exchange material during the low purchase price, the small space requirement with large heat exchangers area and the high efficiency of the heat according to the invention are important evaluation criteria.

In the following the invention based on the in the drawing Exemplary embodiments shown in a schematic manner explained in more detail. Show it

Figure 1 is a perspective view of a heat exchanger through which the counterflow principle can flow through its end faces.

FIG. 2 shows the cross-sectional profile of a hollow profile plate of the heat exchanger according to FIG. 1;

FIG. 3 is an enlarged perspective view of the exchanger unit of the heat exchanger according to FIG. 1 consisting of a hollow profile plate and spacers;

FIGS. 3 to 6 alternative embodiments of a Austau shaving unit in the representation of FIG. 3;

Fig. 7 is a schematic of an arrangement of the heat exchanger in an air-technical installation;

Fig. 8 is a perspective view of an existing from a hollow profile plate, spacers and a flow reversing chamber cooler unit of an evaporative cooler;

Fig. 9 is a schematic sectional view through a flow-through evaporator according to the countercurrent principle;

Fig. 10 is a schematic representation of an air conditioning system for cooling a building, consisting of a heat exchanger according to FIG 1 and an evaporative cooler according to FIG. 9.

FIG. 11a-c show three further alternative embodiments of hollow plates for producing a exchanger unit in a perspective view;

Fig. 12, the hollow plate of Fig 11a in a perspektivi rule exploded view.

Figure 13 is a perspective view of a heat exchanger through which flow through its longitudinal sides according to the countercurrent principle.

FIG. 14a and b two complementary Austauschereinheiten of the heat exchanger of Figure 1 in an enlarged per spectral representation TiVi shear.

Fig. 14c is a sectional view taken along section line CC of FIG. 14b;

Fig. 15 is a plan view of a heat exchanger accordingly Figure 13 with two fans .

FIG. 16 is a top view of the heat exchanger according to FIG. 15 with fans driven by a motor;

Fig. 17 is a plan view of a heat exchanger modified compared to Figs. 15 and 16.

The heat exchanger 10 shown in Fig. 1 consists essentially of a plurality of alternately arranged stack-shaped, rectangular in profile hollow profile plates 12 and spacers 14 , the Hohlprofilplat th 12 are interspersed with flow channels 16 of a medium and with their serving as heat transfer surfaces Broad side walls 18 are in thermal contact with counterflow channels 20 of another medium arranged between the successive plates 12 . The Wärmetau-supplying media are openings 22 , 22 ', 24 , 24 ' of the plate stack 30 in two separate streams 26 , 28 on and off again via the front inlet and outlet openings and are thereby within the plate stack 30 according to the countercurrent principle on the heat transfer surfaces passed along.

The individual hollow profile plates 12 have an elongated narrow rectangular profile with thin-parallel broad side walls 18 and transverse between the wide side walls 18, spaced at equal intervals separating webs 32. The through the wide side walls 18 and dividers 32 square flow channels 16 thus enforce in a mutually parallel, rectilinear arrangement, the hollow profile plate 12 and open at the end sides in an inlet and outlet opening 22 ', 24 '.

In each case a hollow profile plate 12 and the spacers 14 arranged on one of its broad side walls 18 together form a structural and functional unit of the heat exchanger 10 . Such exchanger units 34 , which can be joined together or stacked in a freely selectable number, can be flowed through in opposite flow directions by the media via the flow channels 16 and the inlet and outlet side of the spacers 14 limited th counterflow channel 20 . They can be realized in various embodiments while maintaining the countercurrent principle, some of which are described below.

In the embodiment shown in FIG. 3, the spacers 14 consist of elongated, parallelogram-shaped hollow profile plate sections or plate strips 15 , the longitudinal edges 36 of which run obliquely to the separating webs 32 . The plate strips 15 are fastened to the broad side wall 18 of the hollow profile plate 12 by suitable connecting means, for example welded or glued. They are arranged at the same distance from one another along the plate te 12 and extend with their longitudinal edges 36 over substantially the entire plate height, that is, the vertical extent of the hollow profile plate 12 in the arrangement shown Darge. The dividers 32 in the panel strip 15 are parallel to the partitions 32 in the hollow section filplatte 12th On the broad side wall 18 of the hollow profile plate 12 are provided in addition to the spacers 14 along the edge edges sealing means which are formed in the embodiment shown as a rod-shaped flat end wall elements 38 . The end wall elements 38 are used for edge sealing of the shear elements 34 delimited by broad side wall surfaces facing successive exchange shear elements 34 . Basically, curable connecting means or potting compounds are also suitable as a sealing means for sealing the space on the edge in a gas-tight manner and rigidly connecting the adjacent hollow profile plates 12 to one another. The arranged on the horizontal, parallel to the flow channels 16 forehead side edges 40 of the hollow profile plates 12 end wall elements 38 extend from diagonally opposite corners of the hollow profile plate 12 to the most distant longitudinal edge 36 of the plate strips 15 and thus each give an inlet or outlet opening 22 , 24th free for one of the media.

In addition to their function as a spacer, the Hohlpro filplattenstreifen 14 also serve to flow a media flow 26 passed through the space through the inlet and outlet opening 22 , 24 (which is illustrated in FIG. 3 by arrows with open arrowheads). In this regard, the two outer plate strips 15 are of particular importance, which separate a space parallelo grammar in its base area as a counterflow channel 20 from wedge-shaped, serving as deflection chambers 42 , 44 inlet and outlet-side spaces. In the inlet-side deflection chamber 42 , the medium flowing in via the inlet opening 22 is deflected at right angles by the separating webs 32 or channel sections 45 of the plate strip 15 adjacent to the deflection chamber 42 and perpendicular to the inflow direction. In this case, the media stream 26 of the plate strip 14 is distributed owing to the wedge-shaped narrowing of the deflecting chamber 42 evenly over the orifices 46 of the channel sections 45 and deflected as individual substreams ge 48 in the counter-flow channel twentieth When flowing through the counterflow channel 20 , the partial flows 48 are separated from one another only in the region of the plate strips 15 by solid walls. On the outlet side of the counterflow channel 20 , the partial streams 48 introduced through the channel sections 45 of the final plate strip 14 into the outlet-side deflection chamber 44 are re-merged with another deflection by 90 ° and discharged through the outlet opening 24 in the same direction as the inflow direction.

For the purpose of heat transfer, the second, warmer or colder medium is passed through the flow channels 16 of the hollow profile plate 12 (arrows with filled tips in Fig. 3). The direction of flow is opposite to the flow of the first medium in the counterflow duct 20 , the heat transfer taking place through the wide side wall 18 of the hollow profile plate 12 serving as a partition and heat transfer surface between the media. The two media flows 26 , 28 run in cross flow only in the narrow area of the deflection chambers 42 , 44 . However, this area can be kept small in relation to the total heat exchange surface by appropriate selection of the flow channel length.

The embodiment shown in Fig. 3a differs from the embodiment of Fig. 3 in that the spacers from a plurality of spaced between the mutually facing broad side surfaces of the hollow profile plates 12 arranged, wavy profiled plate strips 15 ', which together with the neigh bare broadside surfaces substantially parallel to the separating webs 32 of the hollow profile plates 12 form Kanalab sections 45 . Basically, it is possible to form the spacers from not shown, corrugated per filed plates made of plastic or metal, which together with the adjacent broad side walls of the hollow profile plates limit a plurality of parallel to the dividers 32 of the hollow profile plates 12 flow channels 45 .

In the modified embodiment shown in FIG. 4, for example an exchanger unit, instead of a plurality of plate strips 15, a single, parallelogram-shaped hollow profile plate piece 50 is provided, which limits the deflection chambers 42 , 44 with its oblique end faces 52 , 54 , and the sen between the deflection chambers 42 , 44 extending channels 56 in their entirety form the counterflow channel 20 . The hollow profile plate piece 50 has substantially the same base area as the counterflow channel 20 delimited by the plate strips 15 . The partial streams formed at the mouth openings to the inlet-side deflection chamber 42 are always separated from one another in the channels 56 of the hollow profile plate piece 50 by means of solid walls and he therefore does not drive a deflection transverse to the intended flow direction. The hollow profile plate piece 50 increases the dimensional stability of the heat exchanger 10 compared to an individual plate strip 15 , but deteriorates due to the increased thickness of the partition walls between the media, the heat transfer due to the wall thickness of its wide side walls. The media not shown in FIG. 4 is guided according to the principle shown in FIG. 3.

In the exemplary embodiment according to FIG. 5, the spacers 14 consist of molded on the hollow profile plates 12 or extruded together with these, parallel to the flow channels 16 , guide ribs 58 . The guide ribs 58 are arranged with the same longitudinal offset from one another over the height of the hollow plate 12 at a distance from one another and, with their end faces 60, limit the orifices 46 to the deflection chambers 42 , 44 . In their entirety, the guide ribs 58 likewise delimit a parallelogram-shaped counterflow channel 20 which is divided into individual subchannels 62 running between the guide ribs 58 . Therefore, the flow guide takes place in the same way as in the exemplary embodiments shown in FIGS . 3 and 4. As illustrated at the upper most guide rib 58 can flow Hinder nit 64 to the guide ribs 58 are fitted to produce a turbulen th flow, the heat transfer area thereby transition improved between the fluidized medium and the Heat Transf.

Fig. 6 shows an embodiment in which the flow management is modified such that both media are each passed through a deflection chamber 42 , 44 and are deflected in their flow by 90 °. For the hollow profile plate-side flow, the deflection chamber 42 is formed by a wedge-shaped plate end piece 66 , the channel cables 68 of which are sealed gas-tight and which is attached to the inlet-side end face of the hollow profile plate 12 . Instead of an end piece 66 , a wedge-shaped recess can also be provided in the plate 12 . In the embodiment shown in FIG. 4, the end piece 66 is fastened to a spacer 14 , which is formed from a rectangular section 70 and is attached to the hollow profile plate 12 with lateral coverage of the flow channel-side deflection chamber 42 . The plate section 70 serves on the other hand as the end of the counterflow channel 20 and for the straight-line discharge of the media flow 28 passed through it. The inlet side of the counterflow channel 20 is delimited by a parallelogram-shaped plate strip 15 , which deflects the incoming flow 28 at a right angle in the manner described with reference to the exemplary embodiment according to FIG. 3.

All of the above-described exemplary embodiments have the common principle that the media streams 26 , 28 can be supplied and discharged through the deflection in the deflection chambers 42 , 44 at different end faces of the exchanger unit 34 . In this way, the respective inlet and outlet openings 22 , 22 ', 24 , 24 ' of a heat exchanger 10 forming group of exchanger units 34 can be easily connected in groups together with a connection piece to an external channel. The Darge presented flow directions of the flow or counterflow channels 16 , 20 are reversible. Especially when using the heat exchanger 10 for heat recovery from Fortge conducted indoor air, there are particularly simple connection options by flanging the mostly formed as rectangular shafts external channels directly on the end faces of the plate stack 30 .

Fig. 7 shows the use of the heat exchanger 10 in an air conditioning system 72 , which is intended to supply a building room 74 with cooled outside air. The outside air stream 76 to be cooled and the exhaust air stream 78 having a lower temperature are passed to the inlet side of the heat exchanger 10 . In the heat exchanger 10 there is a heat transfer from the outside air 76 to the exhaust air 78 , ie the "residual coolness" of the exhaust air, which would be uselessly lost in normal room ventilation, can be used for pre-cooling the outside air. The thus cooled outside air stream 76 is further cooled by the evaporator 80 of a refrigerant circuit 82 of the air conditioning system 72 and supplied to the room 74 to be air-conditioned as a supply air stream 84 . On the other hand, the heated by the outside air stream 76 within the heat exchanger 10 , but not yet fully adjusted in temperature to the outside temperature exhaust air stream 78 is used for further cooling of the condenser 86 of the refrigerant circuit 82 and only then released as exhaust air stream 88 . For influencing the mass flow relationship between th rule outer air stream 76 and the exhaust air flow 78 and thus the heat exchange performance of the heat exchanger 10, the air stream 78 through a valve with an adjustable throttle 89 provided bypass channel 90 partially branched off and be admixed as return air flow 92 to the supply air flow 84th

The use of the heat exchanger 10 described above is mainly possible during the summer months. At low outside temperatures, however, the heat contained in the exhaust air can be recovered in the heat exchanger by preheating the outside air. The heat transfer takes place in the opposite direction. When the exhaust air flow is humid (humidifier 94 ) and there is strong cooling, the saturation temperature is reached and the moisture contained in the exhaust air never affects the latent heat of condensation on the heat transfer surfaces.

This reduces the further cooling of the exhaust air, d. H. the temperature difference between the outside and exhaust air current and thus the efficiency is higher than without condensers station. In addition, the downed water film changes the Interface conditions on the heat transfer surfaces and therefore improves heat transfer.

The cooler unit 100 shown in Fig. 8 has in principle the same structure as the exchanger unit of Fig. 3, wherein instead of the inlet and outlet openings 22 and 24 'a flow reversal chamber 102 is provided at one end of the cooler unit 100 , which from the hollow profile plate 12 ends escaping media flow in the counterflow channels 20 . The medium is thus directed to itself through the cooler unit 100 according to the counterflow principle. To achieve cooling of the medium, a number of water spray nozzles 104 are arranged in the flow reversal chamber 102 , which moisten the media stream 106 emerging from the hollow profile plate 12 and thereby bring about an adiabatic, evaporative cooling of the medium by utilizing the evaporation enthalpy of the water. In addition to the water spray nozzles 104 in the flow reversal chamber 102, a water storage element 108 consisting of a natural or synthetic fiber fabric, through which the medium can flow, is provided, which leads to a further loading of the media stream with moisture up to its saturation. The water storage element 108 is moistened by means of the water spray nozzles 104 .

The operation of the cooler unit 100 is as follows: The inlet opening 22 'of the hollow profile plate 12 is acted upon with the media flow to be cooled, for example the (dry) exhaust air flow from a building room. This reaches ge through the multitude of flow channels 16 in the loading area of the flow reversal chamber 102 , where it is moistened by means of the water spray nozzles 104 and the water storage element 108 and deflected into the counterflow channels 20 . The humidification of the media flow leads to an adiabatic cooling of the medium, whereby heat is removed from the media flow by the evaporation of the water. As a result, the relative humidity of the medium increases while its temperature drops. The media stream cooled in this way passes through the counterflow channels 20 , with heat exchange taking place via the heat transfer surface 18 with the media stream in the Hohlpro filplatte 12 , so that a pre-cooled media stream enters the flow reversal chamber 102 . The media flow in the counterflow channels 20 mainly absorbs the heat without substantial temperature increase to evaporate an excess of water. In this case, even a water film wetting the heat transfer surface 18 can occur.

The cooler unit 100 combines the direct evaporative cooling with the indirect evaporative cooling via the heat transfer surface 18 according to the countercurrent principle and thus achieves a high degree of efficiency.

The evaporative cooler 110 ( FIG. 9) consists, analogously to the heat exchanger 10 of FIG. 1, of a freely definable number of stacked cooler units 100 , the flow reversal chamber 102 extending over the entirety of the cooler units 100 . The medium to be cooled is fed to the inlet openings 22 'of the hollow profile plates 12 by means of a blower 112 and leaves the evaporator cooler 110 through the outlet openings 24 of the counterflow channels 20 , from where it can be fed via a collecting duct to a white recovery, for example in an air conditioning system according to FIG. 10.

The system of FIG. 10 is used for cooling the building space 114, wherein the filled by the arrows with the tips illustrated, is passed cool exhaust air stream for further cooling through the evaporative cooler 110 and is supplied to the outlet from the latter via the connecting shaft 116 meaustauscher the Wär 10 . The warm supply air flow illustrated by the arrows with open tips is directed in counterflow to the cooled exhaust air flow while cooling through the heat exchanger 10 by means of the fan 118 into the room 114 , which is thus supplied with dry and cool fresh air.

The heat exchanger 10 shown in FIG. 13 has a large number of alternating stacks arranged one above the other, rectangular hollow plates 12 ', 12 '', which can in principle be constructed in the manner shown in FIGS. 11a to c.

The hollow plates 12 ', 12 ''shown in Fig. 11a and b' hen best of a flat base plate 100 and a zigzag or corrugated profile, broadly on mutually parallel contact lines with the base plate 100 with the formation of flow channels 16 ', 16 ''Or corresponding Ge counterflow channels 20 ', 20 '' connected profile plate 102nd The base plate 100 and the profile plate 102 can be composed of two parts in the sense of FIG. 12 and glued or welded to one another. However, they can also be produced in one piece, for example in the extrusion or extrusion process.

In the embodiment of FIG. 11c, the hollow consists plate 12 ', 12' 'of a flat base plate 100 and a plurality of 100 projects over a major surface of the base plate, mutually parallel guide ribs 104th The base plate 100 and the guide ribs 104 are also expediently produced in this exemplary embodiment as a one-piece extrusion or extruded part made of plastic or metal.

To complete the exchanger units 12 ', 12 ''who bent the side edges 106 of the base plate 100 to the side of the profile plate 102 by 90 ° in the sense of FIGS. 14 a to c and dimensioned such that they one of the maximum profile depth of the profile plate 102 have the appropriate width. In addition, the profile plates 102 are cut obliquely to form the steering chambers 42 , 44 and the orifices 46 . Next to form the inlet and outlet openings 22 , 24 of the longitudinal side edge 106 is separated at the point in question. The exchanger units 12 ', 12 ''for the various media are provided by appropriately cutting the profile plates 102 at the mouth openings 46 with differently oriented deflection chambers 42 , 44 and inlet and outlet openings 22 , 24 . Through the profile plates 102 , the flow channels or countercurrent channels of an exchange unit are divided into two channel areas 16 ', 16 ''and 20 ', 20 '', of which the channel area 16 ', 20 ' to the base plate 100 of the exchanger element in question is open , while the channel area 16 '', 20 '' to the base plate 100 of the adjacent exchanger unit is open. The aufeinan of the stacked hollow plates 12 ', 12 ''are connected airtight at the joints of their side edges 106 .

In the embodiments according to FIGS. 13 through 16, the flow channels 16 ', 16' 'and the counter-flow channels 20', 20 '' on the input side and output side are each connected to a deflection chamber 42, 44, so that the inlet and outlet openings 22, 24 of Hollow plates stacked one above the other in the vicinity of the two stack ends, alternately pointing to one or the other long side of the hollow plates 12 ', 12 ''. The supply of the two exchange media (arrows 108 and double arrows 110 ) takes place in parallel from one long side of the exchanger, while the removal of the two exchange media also takes place in parallel on the other side of the exchanger. The blowers 112 , 114 required for this are driven in the exemplary embodiment according to FIG. 16 by a common motor 116 .

The embodiment according to FIG. 17 differs from that according to FIG. 15 in that only three of the inlet and outlet-side media streams are directed in parallel, while the fourth media stream is oriented perpendicularly to this. This is made possible by an appropriate design of the deflection chambers 42 , 44 within the heat exchanger units.

In summary, the following can be stated: The invention relates to a heat exchanger 10 through which the countercurrent principle can flow, for two gaseous media of different temperatures. The heat exchanger has stacked hollow plates 12 which are spaced from one another and which have heat transfer surfaces with their broad side walls 18 and are penetrated by mutually parallel flow channels 16 of one medium, while counterflow channels 20 of the other medium run in the area between the hollow plates 12 . For flow deflection of the media streams supplied and discharged separately from one another at different end faces of the hollow plate stack 30 , deflection chambers 42 , 44 are provided which are arranged on opposite sides of the hollow plates. The hollow plates 12 are formed as extruded or extruded hollow profile plates made of plastic or metal, which have a plurality of the flow channels ( 16 ) delimiting, between their broad side walls ( 18 ) formed, mutually parallel dividers ( 32 ).

Claims (38)

1. Heat exchanger for two or more, preferably gaseous media of different temperatures, with two through heat transfer surfaces ( 18 ) separated from each other, from the two media via respective inlet and outlet openings ( 22 , 24 , 22 ', 24 ') according to the counterflow principle Flow-through groups of flow channels ( 16 ), several stacked spaced apart, with their wide side walls ( 18 ) forming the heat transfer surfaces, parallel flow channels ( 16 ) of a medium penetrated hollow plates ( 12 ), countercurrent channels running between the hollow plates ( 20 ) of the other medium and two groups of oppositely arranged deflecting chambers ( 42 , 42 ) arranged on opposite sides of the hollow plate stack ( 30 ), open on the edge side and opening at outlet openings ( 46 ) into the flow channels ( 16 ) or counterflow channels ( 20 ). 44) on the muzzle openings (46) of one of the media under flow diversion through are can flow, characterized in that the Hohlplat ten (12) or extruded or extruded hollow profile plates are formed from plastic or metal, which delimits a plurality of the flow channels (16) between its Have broad side walls ( 18 ) arranged, mutually parallel dividers ( 32 ). 2. Heat exchanger according to claim 1, characterized in that the hollow profile plates ( 12 ) consist of an extruded plastic from the group of polypropylene, polyethylene, polyvinyl chloride, polystyrene, ABS. 3. Heat exchanger according to claim 1, characterized in that the hollow profile plates ( 12 ) consist of an extruded metal from the group aluminum, aluminum alloys gene. 4. Heat exchanger according to one of claims 1 to 3, characterized in that between mutually facing broad side walls ( 18 ) of the hollow profile plates ( 12 ) from spacers ( 14 ; 15 , 50 , 58 , 70 ) are arranged, which the counterflow channels ( 20 ) limit at least in sections. 5. Heat exchanger according to claim 4, characterized in that the spacers from several, in the flow direction at a distance from each other between the facing broad side walls ( 18 ) of the hollow profile plates ( 12 ) arranged strip-shaped hollow profile plates from sections ( 15 ), the separating webs ( 32 ) run essentially parallel to the dividers ( 32 ) of the Hohlpro filplatten. 6. Heat exchanger according to claim 5, characterized in that the strip-shaped hollow profile plate sections ( 15 ) with their cross or oblique to their separating webs ( 32 ) extending longitudinal edges ( 36 ) Chen in wesentli across the entire width of the hollow profile plates ( 12 ) and limit the deflection chambers ( 42 , 44 ) on the mouth side to the counterflow channels ( 20 ). 7. Heat exchanger according to claim 4, characterized in that the spacers consist of wavy profiled th plates made of plastic or metal, which together with the adjacent broad side walls of the hollow profile plates ( 12 ) a plurality of parallel to the separating webs ( 32 ) running flow channels ( 45 ) limit. 8. Heat exchanger according to claim 4, characterized in that the spacers from several, in the flow direction at a distance from each other between the facing broad side surfaces ( 18 ) of the Hohlprofilplat th ( 12 ) arranged, wavy profiled plat tenstreifen ( 15 '), which together with the adjacent broadside surfaces ( 18 ) substantially parallel to the separating webs ( 32 ) of the hollow profile plates ( 12 ) limit ver running channel sections ( 45 ). 9. Heat exchanger according to claim 8, characterized in that the wavy profiled plate strips ( 15 ') with their transverse or oblique to the separating webs ( 32 ) extending longitudinal edges ( 36 ) substantially over the entire width of the hollow profile plates ( 12 ) and limit the deflection chambers ( 42 , 44 ) on the mouth side towards the counterflow channels ( 20 ). 10. Heat exchanger according to claim 4, characterized in that the spacers ( 14 ) from on the broad sides ( 18 ) of the hollow profile plates ( 12 ) molded, par allel to the flow channels ( 16 ) extending Leitrip pen ( 58 ). 11. Heat exchanger according to claim 10, characterized in that the guide ribs ( 58 ) with the same longitudinal offset to each other over the height of the hollow profile plates ( 12 ) are arranged at a distance from one another and with their end faces ( 60 ) the mouth openings ( 46 ) of the order limit steering chambers ( 42 , 44 ). 12. Heat exchanger for two or more, preferably gaseous media of different temperatures, with two heat transfer surfaces ( 18 ) separated from one another, from the two media via respective inlet and outlet openings ( 22 , 24 , 22 ', 24 ') according to the counterflow principle flow-through groups of flow channels ( 16 ), a plurality of stacked spaced apart, with their wide side walls ( 18 ) forming the heat transfer surfaces, parallel flow channels ( 16 ) of a medium penetrated by hollow plates ( 12 , 12 ', 12 '') , between the hollow plates running Ge flow channels ( 20 ) of the other medium and two on opposite sides of the hollow plate stack ( 30 ) arranged, open on the edge and at Mündungsöffnun gene ( 46 ) into the flow channels ( 16 ) or countercurrent channels ( 20 ) opening groups of plates separate deflection chambers (42, 44) over the muzzle openings steering of one of the media under Strömungsum (46) can flow, characterized in that the hollow plates (12 ', 12' ') each sisplatte from a flat Ba (100) and one being a zigzag or Wellenpro having fil, broadly on mutually parallel contact lines with the base plate ( 100 ) to form the flow channels ( 16 ', 16 '') or counterflow channels ( 20 ', 20 '') connected profile plate ( 102 ) are formed. 13. Heat exchanger according to claim 12, characterized in that the base plate ( 100 ) and the profile plate ( 102 ) are formed as a one-piece extrusion or extrusion made of plastic or metal. 14. Heat exchanger according to claim 12, characterized in that the profile plate ( 102 ) and the base plate ( 100 ) are formed as separate molded parts made of plastic or metal, which are glued or welded together at their contact lines. 15. Heat exchanger according to one of claims 12 to 14, characterized in that the preferably rectangular base plate ( 100 ) on its side edges ( 106 ) is preferably bent to the side of the profile plate ( 102 ) by about 90 °. 16. Heat exchanger according to claim 15, characterized in that the bent side edges ( 106 ) of the base plate ( 100 ) have a width corresponding to the maximum profile depth of the profile plate ( 102 ). 17. Heat exchanger according to claim 15 or 16, characterized in that the bent side edges ( 106 ) are interrupted in the region of the inlet and outlet openings. 18. Heat exchanger for two or more, preferably gaseous, media of different temperatures, with two heat transfer surfaces ( 18 ) separated from one another, from the two media via respective inlet and outlet openings ( 22 , 24 , 22 ', 24 ') according to the countercurrent principle flow-through groups of flow channels ( 16 ), several spaced-apart, with their wide side walls ( 18 ) forming the heat transfer surfaces, parallel flow channels ( 16 ) of a medium penetrated by hollow plates ( 12 ', 12 ''), between the hollow plates running counter current channels ( 20 ) of the other medium and two on opposite sides of the hollow plate stack ( 30 ) arranged, open on the edge and at orifices ( 46 ) into the flow channels ( 16 ) or counter-current channels ( 20 ) groups of plates of each other ge separated deflection chambers ( 42 , 44 ) which over the orifices ( 46 ) can be flowed through by one of the media under the direction of flow, characterized in that the hollow plates ( 12 ', 12 '') each consist of a flat base plate ( 100 ) and a plurality of over a wide side surface of the base plate , under Licher limitation of the flow channels ( 16 ) or counterflow channels ( 20 ) parallel to each other leading fins ( 104 ) are formed. 19. Heat exchanger according to claim 18, characterized in that the base plate ( 100 ) and the guide ribs ( 104 ) are formed as one-piece extrusion or extrusions made of plastic or metal. 20. Heat exchanger according to one of claims 1 to 19, characterized in that the deflection chambers ( 42 , 44 ) in groups via an inlet or outlet opening ( 22 , 24 ) to opposite, parallel to the flow channels end faces of the plate stack ( 30 ) are open towards the edges and can be flowed through with a right-angled deflection of the media flows ( 26 , 28 ). 21. Heat exchanger according to one of claims 1 to 20, characterized in that the deflection chambers ( 42 , 44 ) are wedge-shaped in outline and are adjacent to the inlet and outlet opening ( 22 , 24 ), narrow-angle enclosing an acute angle Boundary surfaces extend over the entire height of the hollow profile plates ( 12 ). 22. Heat exchanger according to one of claims 1 to 21, characterized in that the deflection chambers ( 42 , 44 ) on one of their narrow-side boundary surfaces in the mouth openings ( 46 ) of the flow channels ( 16 ) or Ge counterflow channels ( 20 ) open, and that the other narrow-sided boundary surface is sealed gas-tight by an end wall ( 38 ). 23. Heat exchanger according to one of claims 1 to 22, characterized in that the counterflow channels ( 20 ) on the inflow and outflow sides open into one of the two groups of deflection chambers ( 42 , 44 ) and the flow channels ( 16 ) at inlet and outlet openings ( 22 ', 24 ') end on opposite end faces of the hollow plate stack ( 30 ), or vice versa. 24. Heat exchanger according to one of claims 1 to 23, characterized in that the flow channels ( 16 ) on the aisle side and the counterflow channels ( 20 ) on the outlet side are connected to one of the groups of deflection chambers ( 42 , 44 ), or vice versa. 25. Heat exchanger according to one of claims 1 to 24, characterized in that the hollow plates ( 12 ) have quite angular, in the direction of the flow channels ( 16 ) stretched, preferably thin-walled broad side walls ( 18 ). 26. Heat exchanger according to one of claims 1 to 25, characterized in that the countercurrent channels ( 20 ) forming spaces between the hollow plates ( 12 ) on the end faces of the stack of hollow plates ( 30 ) are closed gas-tight. 27. Heat exchanger according to one of claims 1 to 26, characterized in that the flow channels ( 16 ', 16 '') and the counterflow channels ( 20 ', 20 '') on the input side and on the output side each with one of the groups of deflection chambers ( 42 , 44 ) are connected, and that the inlet and outlet openings ( 22 , 24 , 22 ', 24 ') of the sandwich-like stacked hollow plates ( 12 ', 12 '') in the vicinity of the two ends of the stack alternately towards opposite long sides of the Hollow plates ( 12 ', 12 '') have. 28. Heat exchanger according to one of claims 1 to 27, characterized in that the flow channels ( 16 ) are connected on the inlet and outlet sides to one of the groups of deflection chambers ( 42 , 44 ) that the counterflow channels ( 20 ) only one or are connected on the output side to one of the groups of deflection chambers and that the inlet and outlet openings ( 22 , 24 , 22 ', 24 ') of the hollow plates ( 12 ', 12 '') stacked on top of one another in the manner of sand are alternately at opposite ends of the stack only at one end of the stack of the hollow plates. 29. Heat exchanger according to one of claims 1 to 28, characterized by in the flow channels ( 16 ) and / or counterflow channels ( 20 ) arranged flow obstacles ( 64 ) for generating a turbulent flow. 30. Heat exchanger according to one of claims 1 to 29, characterized in that the flow channels ( 16 ) and the countercurrent channels ( 18 ) of a pair or stack of hollow section plates communicate with one another in the region of one of their orifices ( 46 ) to form a flow reversal chamber ( 102 ). 31. Heat exchanger according to claim 30, characterized in that the flow reversal chamber ( 102 ) can be opened with water. 32. The heat exchanger according to claim 30 or 31, characterized in that a water storage element ( 108 ) through which the medium can flow is arranged in the flow reversal chamber. 33. Heat exchanger according to claim 32, characterized in that the water storage element ( 108 ) consists of a Fa sergewebe or a nonwoven fabric. 34. Heat exchanger according to claim 33, characterized net that the fiber fabric or nonwoven fabric made of textile  There is fiber material. 35. Use of a heat exchanger according to one of claims 1 to 34 in air conditioning systems ( 72 ) for heating or cooling a supplied outside air stream ( 76 ) using the heat content of an exhaust air stream ( 78 ). 36. Use according to claim 35, wherein the outside air flow ( 76 ) or exhaust air flow ( 78 ) using the evaporation enthalpy of a slightly evaporating cooling liquid, especially water, is additionally cooled. 37. Use according to claim 35 or 36 in combination with an evaporator ( 80 ) and a condenser ( 86 ) of an air conditioning system ( 72 ), the outside air flow ( 76 ) through the evaporator ( 80 ) and the condenser ( 86 ) through the exhaust air flow ( 88 ) is additionally cooled. 38. Use according to one of claims 35 to 37, characterized in that the throughput of the outside air flow ( 76 ) is adjusted by admixing a branched from the exhaust air flow ( 78 ) and the supply air flow ( 84 ) admixed circulating air flow ( 92 ).