EP1588114A1 - Echangeur de chaleur a air et a eau a parcours partiels de l'eau - Google Patents

Echangeur de chaleur a air et a eau a parcours partiels de l'eau

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Publication number
EP1588114A1
EP1588114A1 EP03789429A EP03789429A EP1588114A1 EP 1588114 A1 EP1588114 A1 EP 1588114A1 EP 03789429 A EP03789429 A EP 03789429A EP 03789429 A EP03789429 A EP 03789429A EP 1588114 A1 EP1588114 A1 EP 1588114A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
water
water flow
air
heat
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
EP03789429A
Other languages
German (de)
English (en)
Other versions
EP1588114B1 (fr
Inventor
Heinz Schilling
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.)
Heinz Schilling KG
Original Assignee
Heinz Schilling KG
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 Heinz Schilling KG filed Critical Heinz Schilling KG
Publication of EP1588114A1 publication Critical patent/EP1588114A1/fr
Application granted granted Critical
Publication of EP1588114B1 publication Critical patent/EP1588114B1/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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • 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
    • F28D9/0081—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 a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction

Definitions

  • the invention relates to a heat exchanger, in particular a counterflow layer heat exchanger for heat exchange between gaseous and liquid media, which is preferably designed in a modular or modular block design, and a method for operating a heat exchanger.
  • Such heat exchangers are used to transfer amounts of heat and their temperature potentials from one heat transfer medium to another heat transfer medium.
  • One medium is preferably a gas, in particular air, and the other medium is a liquid fluid, preferably water or also water / antifreeze mixtures or other suitable liquid fluids.
  • a typical air / water glycol heat exchanger is used frequently.
  • the ratio of the heat capacity flows is represented, for example, in an air / water heat exchanger by the so-called water ratio.
  • m is the mass and c is the specific heat capacity of the corresponding medium.
  • the enthalpy difference is decisive instead of cm «.
  • the air volume flows and external dimensions of a heat exchanger module are often specified by the customer, so that the corresponding water volume flow must be determined and implemented constructively.
  • it can be particularly in the case of low air volume flows and in the construction of a heat exchanger with conventional water pipe cross sections of e.g. 8 - 15 mm inside diameter also means that the flow velocity becomes too low with the necessary water volume flow, so that the heat transfer resistance on the inside of the pipe increases and thus the heat transfer is greatly reduced.
  • the heat exchangers have to meet the customer's design requirements individually adjusted to adjust the water value ratio to the optimal value and to achieve a sufficiently high water flow rate.
  • the object of the invention is to provide a universal heat exchanger, in particular in a modular design, in which a necessary ratio of the heat capacity flows, a sufficient flow rate of the liquid medium within the media-carrying pipes and high efficiency and ease of cleaning can be ensured in a structurally simple manner.
  • a heat exchanger or, in the case of a modular construction, a module area of a heat exchanger between two air flow areas has a water flow area with water flow channels, which are preferably arranged in one plane from the air inlet to the air outlet.
  • the division into air flow areas and water flow areas already means that no piping is provided within the air flow areas, so that the air can flow through the heat exchanger undisturbed within these areas.
  • the preferred arrangement within the water flow area with water flow channels lying in one plane, which are all arranged in parallel in the air flow direction, in particular one behind the other, preferably as close as technically possible, reduces the air flow resistance, since essentially only the first water flow channel in the air flow direction flows against the air becomes.
  • the space between two adjacent flow channels will preferably be smaller than half the width or half the diameter of a flow channel.
  • the water path through the heat exchanger can furthermore preferably be divided or divided into a plurality of parallel part water paths by interconnecting a plurality (at least two) of parallel water flow channels.
  • This design of the heat exchanger enables standard heat exchanger modules to be made available, which, depending on the required air inflow surface or the resulting air volume flow, can be supplied to a required water volume flow with a sufficiently or sufficiently high flow rate can be adapted without the need for complex redesign or redesign of such a heat exchanger module.
  • a heat exchanger according to the invention has a plurality of water flow channels which are arranged next to one another, in particular parallel, and which, in the cross-countercurrent principle, guide the water through the heat exchanger in particular on one level.
  • the water path through the heat exchanger leads in accordance with the countercurrent principle from the air outlet of a heat exchanger to the air inlet, the water flow channels being transverse to the air direction and accordingly the water path or the water flowing against the air at the same time crossing the air flow several times, as a result of which the cross-countercurrent principle is established ,
  • this combination allows the water path to be divided into several parallel partial water paths, each partial water path leading through a water flow channel.
  • the effective cross section in the water path within the heat exchanger can be effectively increased, since the effective cross section of the water path results from the sum of the cross sections of the individual partial water paths or water flow channels.
  • each water flow channel is equipped with the same cross-section (in the case of round pipes with the same diameter)
  • the effective cross-section of the waterway can be compared to one, for example, if two water flow channels are combined in parallel and thus the waterway is divided into two parallel partial waterways that cross the airflow single water flow channel can be doubled.
  • the water flow channels are combined in such a way that in at least two combined water flow channels, which are arranged in parallel next to one another, the water flows in the same direction and crosses the air flow.
  • the air cross-section for example, is significantly increased, which also follows a change in the water volume flow in order to maintain the water value ratio, then several water flow channels can be combined in terms of circuitry in parallel to one water path or the water path through the heat exchanger can be divided into several partial water paths at least in one section to be able to use a larger volume of water per unit of time without increasing the flow velocity of the water within the combined partial waterways.
  • a required amount of water flowing through the heat exchanger per unit time can accordingly be obtained for a given air inflow surface of a heat exchanger or, in the case of constant heat exchanger heights, for a given width of a heat exchanger, by dividing the water path into a plurality of parallel partial water paths or, in particular, one behind the other. Flow channels matched become. Conversely, by selecting the lowest possible partial water quantities in a flow channel and possibly combining the flow channels, any air quantity / module or module width or module area can be achieved.
  • each water flow channel Due to the fact that the cross-sectional area of each water flow channel can be reduced when the water path is divided into a plurality of parallel flow channels, the air flow direction also has a smaller inflow area of the water flow channels lying transversely to the air flow direction, so that this arrangement of as many water flow channels as possible results in a lower air flow resistance of the heat exchanger is achieved in operation. Accordingly, very effective heat exchangers can be produced with this construction.
  • a heat exchanger module can be designed such that the air and water flow areas are each formed from separate air and water flow units as separate production units.
  • a heat exchanger according to the invention can be constructed by joining two air flow units with a water flow unit arranged between them, whereby sufficient heat transfer must be ensured.
  • the required heat transfer can take place here through a wide variety of thermally suitable connection measures, for example by welding, soldering, gluing, pressing, grinding etc. of the individual production units to one another.
  • the water flow area in the form of a heat-conducting plate with water flow channels arranged therein.
  • the heat conducting plate can be designed in different ways.
  • the heat-conducting plate can be constructed from a solid material which has a plurality of water flow channels arranged parallel to one another, which e.g. through holes or other types of channels within the material thickness of the solid material.
  • the heat conducting plate can e.g. be formed from a plurality of rectangular tubes arranged in parallel next to one another and connected to one another.
  • a plurality of parallel flow channels which together form a waterway, can preferably be formed within the rectangular tubes.
  • These rectangular tubes can e.g. be connected to one another by adhesive bonding, welding, soldering, tongue and groove, and thus form a heat conducting plate in a side-by-side arrangement which has a height which corresponds to the height of each individual rectangular tube.
  • the individual rectangular tubes preferably each have the same overall height in order to ultimately form a heat-conducting plate with two flat surfaces, on each of which the air flow units can be arranged.
  • the rectangular tubes can preferably have different widths and thus cross sections with the same overall height, the tubes also being able to have a different number of flow channels located therein depending on the width.
  • the heat-conducting plate consists of two sub-plates that can be connected or connected to one another to form, which form water flow channels arranged in between when they are joined together due to their shape.
  • the partial plates have webs forming channel walls on the inner sides facing each other, so that the water flow channels form when the two partial plates are joined together.
  • the partial plates can be designed as sheets into which depressions are stamped, which in turn form the channels when the individual plates are joined together. Any number of different constructive measures are conceivable here to constructively design the heat-conducting plate.
  • the invention described here is not limited to the aforementioned three alternative and preferably used construction options. It is at the discretion of the person skilled in the art to construct a suitable heat-conducting plate which has a plurality of water flow channels which are arranged in parallel next to one another and which in turn can be combined or combined in order to obtain a desired division of the waterway into several partial waterways.
  • Another advantage of this construction is that any dirt deposits within the airflow units can be expelled from the individual airflow channels in a simple manner, since an airflow used for cleaning, e.g. by means of a high-pressure blower or a cleaning steam jet, remains channeled within the air flow channel and cannot escape into neighboring regions. An air flow introduced at the beginning of a heat exchanger will accordingly definitely exit at the corresponding rear end of the heat exchanger without being able to change its direction of flow.
  • the air and water flow areas are formed by the joining together of individual, in particular specially shaped, heat-conducting fins.
  • a heat-conducting lamella accordingly has different sections, preferably at least two sections forming partial areas of an air flow area and at least one section forming a partial area of a water flow area.
  • the assembly of several, in particular identical, heat-conducting fins results accordingly in accordance with the invention Heat exchangers with fully developed air and water flow areas.
  • bores can be provided perpendicular to a lamella surface within a lamella, which each align when a plurality of lamellas are joined and thereby form the water flow channels or form recesses into which separate piping can be inserted.
  • These pipes are heat conductive with the fins e.g. connected by pressing or other suitable measures.
  • a single lamella can have a material thickening with bores arranged next to one another, these material thickenings of a plurality of lamellae forming the water flow region after the joining, and in particular each material thickening having a thickness which corresponds to a desired lamella spacing.
  • a slat can e.g. be produced by rolling out a flat profile towards the ends, the desired material thickness remaining in the central region of this flat profile, in which the bores are provided. It can be provided here that the material thickenings lie close together when individual heat-conducting fins are joined and thus form the water flow area, in particular through the bores.
  • a lamella in another embodiment, can have, for example, a bead-shaped bulge that extends over an entire lamella length and has recesses or bores for receiving tubes that run perpendicular to the lamellae.
  • a heat-conducting material can be used within such a bead-shaped bulge in order to ensure better thermal contact between the tubes to be used therein and the fins.
  • the heat-conducting material can be designed as a heat-conducting tape, which can be pressed or pressed into the bulge.
  • the construction of the heat exchanger also results in at least one separating surface which separates adjacent air flow areas from one another, for example by means of a bead-shaped bulge or at least one material thickening within each fin.
  • the air flowing in an air flow channel formed remains channeled from the beginning to the end of the heat exchanger and cannot escape in other directions. This results in an undisturbed flow pattern with reduced flow resistances and the special cleaning activity described above.
  • the water flow channels arranged next to one another in one plane can be combined in parallel or, after such a combination, can also be divided again.
  • the heat exchanger has a plurality of sections / areas in which the waterway can be divided or divided into a different number of partial waterways by combining a different number of parallel water flow channels.
  • the waterway in a first area of the heat exchanger, can be divided into three partial waterways by combining three water flow channels and in another, for example adjacent area, can be divided into four partial waterways.
  • the division of the waterway into several partial waterways by combining several water flow channels is not restricted to certain areas of the heat exchanger. It can be provided that the waterway at the beginning of a heat exchanger is divided into a certain number of partial waterways or water flow channels and this division is maintained across the entire heat exchanger until the partial waterways are combined again into a waterway at the end of the heat exchanger. Accordingly, several parallel partial waterways, which are realized by the water flow channels interconnected in parallel, e.g. meandering the heat exchanger from start to finish.
  • the combination of several water flow channels can be achieved here according to the invention by various design measures.
  • the water flow channels are realized by distributor pipes arranged on the outside of the heat exchanger.
  • the water flow channels can protrude on the respective end faces of the heat exchanger and can be connected to connecting pieces by pipe bends or transverse flow channels.
  • the water flow channels have internal connections.
  • a type of connection can be selected if the water flow channels and in particular a heat conducting plate is formed by rectangular tubes arranged side by side.
  • the end faces of a heat exchanger can be provided in the area of the end faces of a heat exchanger that a channel wall separating two adjacent water flow channels is removed or removed in order to allow the flowing water to pass from a connection point into two or more water flow channels simultaneously.
  • the end faces of a heat exchanger according to the invention are designed without interfering piping.
  • the water path jumps over a water flow channel provided in the heat exchanger, e.g. to use a measuring device in such a free channel, for example a temperature measuring device or the like.
  • FIGS. 1 and 2 a heat exchanger with air flow units and an intermediate water flow unit in the form of a heat-conducting plate with channel-forming bores arranged transversely to the air direction;
  • Figures 4 - 10 several options for forming a heat exchanger according to the invention by joining identical, specially shaped heat-conducting fins;
  • Figure 11 the formation of a heat conducting plate between
  • FIG. 12 the formation of a heat-conducting plate by means of two partial plates with webs arranged on the mutually facing inner sides for forming water flow channels after the partial plates have been joined;
  • Figure 14 a heat exchanger with a waterway divided into three partial waterways.
  • Figures 1 and 2 show in several different views the structure of a heat exchanger 1 according to the invention from corresponding manufacturing units, two air flow areas 2 being separated from one another by a water flow area 3 in the form of a heat-conducting plate 3.
  • the air and water flow areas constructed as production units 2 and 3 are connected to one another in a heat-conducting manner, so that effective heat transfer between the air and the liquid medium is possible.
  • the person skilled in the art provides a suitable measure for the type of connection, such as grinding, soldering, gluing, welding, pressing, the use of a thermal paste or other suitable measures.
  • Each heat-conducting plate 3 in turn has a multiplicity of bores 5 which run transversely to the air direction L and which extend completely through the heat-conducting plate 3 formed as a solid material in FIGS. 1 and 2 and thus in each case form a water flow channel in order to form a heat exchanger in the cross-countercurrent principle through the parallel arrangement of a plurality of water channels 5.
  • a suitable connection ensures that the water flow channel 5a e.g. water flowing in on the right-hand side of the heat exchanger 1 can flow on the rear side (not shown) into the water flow channel 5b arranged in front of it.
  • the water can thus flow in a meandering shape in the heat exchanger
  • Both the structure of the air flow units and the heat-conducting plate 3 arranged between two air flow units 2 result in a complete separation of the air flows in the two air flow areas 2 and also a separation of the individual partial air flows within the air flow channels 2a, 2b etc. described special cleaning possibility of such a heat exchanger and, due to the undisturbed flow of air, a particularly low pressure drop, which has a noticeable positive effect on energy.
  • FIG. 2 shows that several of the heat exchanger modules shown in FIG. 1, each consisting of two air flow areas and a water flow area arranged between them, can be combined to form a total heat exchanger.
  • an air flow area arranged between two water flow areas or heat-conducting plates 3 has twice the height as an air flow area 2, which adjoins a water flow area or a heat-conducting plate 3 only on one side.
  • FIG. 3 shows various possibilities for combining water flow channels arranged next to one another, which are formed in a heat conducting plate 3, ie dividing the water path into partial water paths in order to achieve an adjustment of the water value ratio or a desired flow rate.
  • three water flow channels 5a, b and c are merged in parallel in terms of circuitry to form a waterway, for which purpose the waterway from the distributor pipe 6 in section A1 is divided into the three partial waterways of the waterflow channels 5a, b, c and after passage through the heat exchanger is brought together again in the opposite collecting pipe 6a in order to immediately carry out a new division in section A2 into the three water flow channels arranged next to it.
  • the water flow channels 5a, b and c according to the summary, the water flows in the same direction across the air flow direction.
  • the combination or division of the water path is realized here by an interconnection provided on the outside of the heat exchanger in the form of a transverse distributor pipe 6 / 6a, which has stubs for the water to enter the heat-conducting plate 3 or for the outlet.
  • FIG. 3 shows an internal connection of the individual water flow channels, only two here Water flow channels 5a and 5b are connected to one another in terms of circuitry to form a waterway.
  • the interconnection takes place in such a way that the material 7 between two water flow channels 5a and b is removed in the region of the end face of a heat exchanger and the opening resulting in the heat conducting plate 3 is closed by a stopper 8. This ensures that the inflowing water is simultaneously distributed to two water flow channels 5a and b, so that these two water flow channels form a water path through the heat exchanger.
  • FIG. 4 shows in several different views that the air and water flow areas of a heat exchanger according to the invention can be formed by assembling individual, in particular specially shaped, heat-conducting fins 10.
  • each heat-conducting lamella 10 or at least a number of lamellae is of identical design and has a material thickening 11 within its lamella height H, which extends over the entire lamella 10.
  • the material thickening 11 is formed approximately centrally in a lamella 10.
  • a plurality of bores 5 arranged side by side are formed perpendicular to the surface of a fin 10 and extend centrally through the material thickening 11 and, after the joining of a plurality of fin 10, form the water path transversely to the air direction of the heat exchanger.
  • a lamella 10 has partial sections of the air and water flow areas which result after a plurality of lamellae have been joined together.
  • the area around the material thickening 11 forms the later water flow area 3 and the areas shown above and below with reference to FIGS. 4 each form part of an air flow area 2.
  • the aligned arrangement of the various bores 5 results in a water flow channel into which either a supplementary tube R is also used or is formed by the material thickenings 11 lying on top of one another in a sealing manner.
  • This construction also makes it clear that the air flow area 2 is completely separated from a water flow area W, so that an overflow of air from one air flow area into another is avoided. Also within an air flow area 2, in particular through the material thickening 11 and through an upper bend of each lamella, separate air flow channels 2a, 2b etc. result, so that the cleaning activity and pressure loss minimization described above is achieved.
  • FIG. 5 shows an essentially identical embodiment, but a single lamella has a much greater height H and several material thickenings are provided within the lamella height in order to form not only several air flow areas but also several water flow areas, each of which is preferably arranged in parallel planes are.
  • each lamella has a bulge, a projection, a bead or other construction 12, so that when several lamellae 10 are joined together, these constructions 12 effectively lie against one another , results in a separating surface T which divides the individual air flow channels 2a, 2b etc. of an air flow area again.
  • FIG. 5 also shows an optional bend 13 at the respective outer ends of each lamella 10, so that such a bend also results in an air flow duct 2a, 2b etc. closed to the outside of the heat exchanger.
  • the thickness of a material thickening 11 within a lamella 10 is selected such that the joining of the individual lamellae 10 results in a spacing between the lamellae which corresponds to the thickness of the material thickening 11.
  • each lamella accordingly gives the periodic structure of a heat exchanger according to the invention after assembly.
  • the material thickening shown in FIGS. 4 and 5, which is only arranged on one side of a lamella, can e.g. can be produced by forming a lamella as an extruded profile or as a rolled flat profile provided with a bulge / bead or a projection.
  • FIG. 6 shows an alternative embodiment of a heat exchanger produced by assembling several identical fins, in which the fin 10 has a material thickening 11 compared to FIG. 4, which extends on both sides of the surface of a fin 10.
  • each material thickening 11 extending within a lamella and extending over its length has a plurality of bores arranged next to one another, which form a part of the entire waterway after being aligned and, if appropriate, using a pipe R pressed therein.
  • a heat exchanger module block can have air flow channels 2 which are closed to the outside in that the the top of each slat 10 is formed as a bevel 13, which lies with its respective end on the surface of an adjacent slat 10. It is also possible to close a non-folded lamella 10 on the upper side by means of a separating surface plate 15, and thus to form the various individual air flow channels 2. Such separating surface plates 15 can also be inserted between individual heat exchanger modules stacked on top of one another, as are shown in FIG. 6, in order to effect the separation of the air flow channels 2.
  • the material thickening 11 of FIG. 6, which is formed on both sides of the lamella 10, has the advantage that the heat conduction through the lamella 10 into the water flow channel 5 or the pipe R used therein by symmetrical heat conduction paths is improved, so that the embodiment according to FIG. 6 is to be regarded as preferred over the embodiment according to FIG.
  • FIG. 7 shows a further alternative embodiment of a heat exchanger composed of a plurality of identical fins, one fin 10, e.g. Has bead-shaped bulge 16, which extends over the entire length of a lamella and forms the later water flow area created after the joining.
  • a heat conducting material e.g. a heat-conducting tape 17 is inserted, which is thermally conductively connected to the lamella 10 by gluing, pressing or similar measures and has bores 5 which form the later water path transverse to the lamella direction.
  • FIG. 7b shows a very simple design of identical lamellae 10, which are completely smooth in their surface and only have bevels at the upper and lower ends for closing the individual air flow channels 2.
  • a flat profile or heat-conducting tape 17 is placed, which in turn has a plurality of bores arranged next to one another, which are aligned with corresponding bores in each lamella 10.
  • An air flow area and water flow area, as described in FIG. 4b, are likewise formed here by joining together a plurality of identical heat-conducting fins and heat-conducting strips 17.
  • FIGS. 8a and 8b show a detailed view of a single lamella 10 according to FIG. 7a, where the heat-conducting tape 17, which has a plurality of bores 5 arranged next to one another, can be seen in the bead-shaped bulge 16.
  • a further tube R can be inserted and heat-conductive with the heat-conducting tape 17 e.g. be connected by pressing.
  • the bends 13 are shown at the top and bottom of the lamella 10 shown, the width of a bend 13 corresponding to the depth of the bulge 16, so that the distance between the individual lamellas 10 is given by this measure.
  • FIG. 9 shows a heat exchanger module unit of greater overall height, in which heat conducting fins according to FIGS. 7 and 8 described above are used. It can also be seen here that a plurality of bead-shaped bulges 16 are provided within a lamella, in each of which a heat-conducting strip 17 is inserted. Within an air flow area 2, each lamella 10 has the construction 12 described above, in order to form a further separating surface T within an air flow area 2 when the individual lamellae 10 are joined together.
  • FIG. 10 shows a special embodiment of individual slats 10, with a bulge 16 being provided over the entire slat length approximately as previously described in FIGS. 7, 8 and 9, 16 being within this bulge circular counter-formations 17 are stamped, which have a circular inner cross section and serve to receive a tube R.
  • the counter-molding 17 provides a resilient elasticity when the water-carrying pipe R is connected to the lamella 10.
  • Each e.g. Bead-shaped bulge 16 within a lamella, as already described above, has a depth which corresponds to the desired spacing of the individual lamellae 10 from one another, as is also the case with the upper and lower fold 13 of each lamella.
  • the bulge 16 which extends over the entire length of the lamella, in turn results in an effective separating surface between the individual air flow areas or the individual air flow channels, so that an overflow of air from one into another air flow area is excluded, and thus the cleaning activity described above and the low air resistance can be achieved.
  • FIG. 10 shows an alternative embodiment to FIGS. 1 and 2, in which the air flow and water flow areas are in turn designed as separate production units.
  • the heat-conducting plate 3 is formed by arranging a plurality of rectangular tubes 5 next to one another, each of which has the same overall height.
  • rectangular tubes 5 in units of several, e.g. three or four rectangular tubes are combined, or a rectangular tube has further inner channel walls for subdivision.
  • the individual rectangular tubes or tube units are suitably connected to one another, for example by welding, with a combination of several rectangular tubes 5 being given in the present case by an internal connection of the individual tubes.
  • This can be done in sections in the area of the end face of a heat exchanger, the separating channel walls between adjacent rectangular tubes, as exemplarily shown at point 20, must be removed, so that here the water flows from a first of four rectangular tubes 5 combined into a second water path II and immediately.
  • the number of combined water flow channels 5 varies within different areas of a heat exchanger, as is the case here e.g. at waterways IV and V is shown.
  • the waterway IV is made up of a total of four rectangular tubes, whereas the waterway V is made up of only three rectangular tubes, so that different flow rates occur at the same volume flow in these two areas of the heat exchanger.
  • the water connection to the entire heat exchanger circuit can be achieved here by an adapter piece 21 which converts the elongated rectangular cross section into a round cross section for distribution to conventional pipes.
  • FIG. 12 shows a further embodiment in which the heat-conducting plate 3 is joined by an upper part plate 3a and a lower part plate 3b.
  • On each of these two partial plates at least one web 22 is provided on the side facing each other, which is opposite a corresponding corresponding web on the respective other partial plate, so that flow channels within the heat-conducting plate 3 result when the upper and lower partial plates are joined.
  • Assembling the plate can be made by conventional measures such as soldering, welding, gluing, pressing, etc.
  • the further structure is essentially as already described in FIG. 11.
  • FIG. 13 shows another alternative of a heat exchanger which is assembled from several identical heat-conducting fins 10.
  • the heat-conducting fins 10 shown here have a very simple structure with only circular shapes 23, which e.g. can be made by punching. These formations 23 form a tubular section pointing away from the lamella surface, into which a tube R can be pressed in a heat-conducting manner. This results in a good intimate thermal contact between the tube R and the lamella via the formation 23.
  • the formation 23 is introduced into the flat surface of the lamella 10, so that there is basically the possibility here that air can pass between two pipes R from an upper air flow channel 2a into a lower air flow channel 2a '.
  • this version represents a construction with a higher pressure loss within the air flow areas, its very simple implementation complies with the basic principles of the invention, by combining several pipes arranged on one level, to be able to change the water value ratio and the flow rate.
  • FIG. 14 shows a sketched arrangement in which the water path is divided into three partial water paths by a heat exchanger at the water inlet WE, which run through the water flow channels 5a, 5b and 5c. While maintaining this division into three partial waterways, the water is meandered through the entire heat exchanger until it is finally merged again into a waterway at the water outlet WA. Accordingly, this is not only divided into several waterways an area / section of the heat exchanger, but across the entire heat exchanger.
  • a cross-section of the flow channels is preferably used, which is 10 to 50% of the connection cross-section of a waterway, the distance between the channel inner walls of a water flow channel to the next being chosen to be preferably smaller than the inner diameter of a pipe or the width of a channel ,
  • the connection cross-section of a waterway is divided over many, in particular as many flow channels as possible with a smaller cross-section, the sum of these smaller cross-sections in particular roughly corresponding to the connection cross-section.
  • the heat exchanger according to the invention therefore has the particular advantage that it can be available in stock in standardized module units and the adaptation to the given external conditions such as air flow, water flow, construction dimensions, the resulting water value ratio and the required flow rates in a simple manner simply by the more or less strong summary of waterways can be set.
  • the heat exchanger according to the invention is accordingly very economical, maintenance-friendly and energy-saving due to the essentially undisturbed airways in the constructions described above, which achieve the cleaning option described by their separation from one another.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur à contre-courant stratifié, utilisé pour l'échange de chaleur entre des milieux gazeux et liquides, de conception modulaire ou de type bloc modulaire. Une zone modulaire comprise entre deux zones d'écoulement d'air (2) présente une zone d'écoulement d'eau (3), munie de canaux d'écoulement d'eau (5), disposés sur un plan, de l'arrivée d'air jusqu'à la sortie d'air. A cet effet, en particulier le parcours de l'eau à travers l'échangeur de chaleur peut être ou est réparti, dans au moins une section/zone (A1, A2), par interconnexion de plusieurs canaux d'écoulement d'eau (5) parallèles, en plusieurs parcours partiels parallèles de l'eau, notamment pour ajuster un rapport de valeur d'eau voulu ou requis. L'invention concerne en outre un procédé d'exploitation d'échangeur de chaleur.
EP03789429.2A 2003-01-31 2003-12-30 Échangeur de chaleur à couches à contre-courant et courant croisé Expired - Lifetime EP1588114B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10304077 2003-01-31
DE10304077A DE10304077A1 (de) 2003-01-31 2003-01-31 Luft-/Wasser-Wärmetauscher mit Teilwasserwegen
PCT/EP2003/014954 WO2004068052A1 (fr) 2003-01-31 2003-12-30 Echangeur de chaleur a air et a eau a parcours partiels de l'eau

Publications (2)

Publication Number Publication Date
EP1588114A1 true EP1588114A1 (fr) 2005-10-26
EP1588114B1 EP1588114B1 (fr) 2013-08-28

Family

ID=32695128

Family Applications (1)

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EP03789429.2A Expired - Lifetime EP1588114B1 (fr) 2003-01-31 2003-12-30 Échangeur de chaleur à couches à contre-courant et courant croisé

Country Status (7)

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US (1) US20060153551A1 (fr)
EP (1) EP1588114B1 (fr)
JP (1) JP4092337B2 (fr)
CN (1) CN1745288B (fr)
AU (1) AU2003294016A1 (fr)
DE (1) DE10304077A1 (fr)
WO (1) WO2004068052A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202005013835U1 (de) * 2005-09-01 2005-11-10 Syntics Gmbh Vorrichtung zum schnellen Aufheizen, Abkühlen, Verdampfen oder Kondensieren von Fluiden
WO2011022738A1 (fr) 2009-08-27 2011-03-03 Gerhard Kunze Echangeur de chaleur liquide-gaz
DE102013003905B4 (de) * 2013-03-08 2020-01-23 Simon Benzler Modulwärmeübertrager in lüftungstechnischen Geräten
US10766097B2 (en) * 2017-04-13 2020-09-08 Raytheon Company Integration of ultrasonic additive manufactured thermal structures in brazements
US20190310030A1 (en) * 2018-04-05 2019-10-10 United Technologies Corporation Heat augmentation features in a cast heat exchanger
CN112060979B (zh) * 2020-08-21 2022-03-29 东风汽车集团有限公司 一种燃料电池车辆的冷却控制方法及装置
RU209585U1 (ru) * 2020-09-07 2022-03-17 Федеральное государственное бюджетное образовательное учреждение высшего образования "Саратовский государственный технический университет имени Гагарина Ю.А." (СГТУ имени Гагарина Ю.А.) Многопоточный трубчатый змеевик
CN114111431A (zh) * 2021-12-25 2022-03-01 上海瀚显空调节能技术有限公司 可同时适用于横流冷却塔和逆流冷却塔的布水装置

Family Cites Families (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2007001A (en) * 1934-03-02 1935-07-02 William E Oakey Extended surface convector
US2054404A (en) * 1935-03-13 1936-09-15 Fedders Mfg Co Inc Refrigeration apparatus
US2098830A (en) * 1935-11-12 1937-11-09 John J Nesbitt Inc Apparatus for the heating of air
US2602650A (en) * 1951-04-12 1952-07-08 Marcotte Louis Philippe Fin type radiator
US2963277A (en) * 1957-11-15 1960-12-06 Licencia Talalmanyokat Finned construction for heat exchangers
US3443634A (en) * 1967-04-06 1969-05-13 Peerless Of America Heat exchangers
CH519151A (de) * 1969-06-13 1972-02-15 Schoell Guenter Rippenrohr, Verfahren zu seiner Herstellung, und Vorrichtung zur Ausführung des Verfahrens
US3990504A (en) 1975-09-29 1976-11-09 International Harvester Company Two stage operation for radiator
JPS57155087A (en) * 1981-03-20 1982-09-25 Hitachi Ltd Manufacture of aluminum heat exchanger
IT8221239V0 (it) * 1981-04-15 1982-03-22 Sueddeutsche Kuehler Behr Scambiatore di calore
US4428418A (en) * 1982-05-17 1984-01-31 Chromalloy American Corporation Heat exchanger fin element with folded over side edges
EP0132237A3 (fr) 1983-06-30 1986-02-05 Renato Ferroni Elément pour l'échange de chaleur entre fluides et radiateur fabriqué avec le dit élément
DE3325230C2 (de) 1983-07-13 1994-03-31 Schilling Heinz Kg Wasser/Sole-Luft-Wärmetauscher
DE3521914A1 (de) * 1984-06-20 1986-01-02 Showa Aluminum Corp., Sakai, Osaka Waermetauscher in fluegelplattenbauweise
DE3433598A1 (de) 1984-09-13 1986-03-20 Heinz Schilling KG, 4152 Kempen Verfahren zur praktischen anwendung des gegenstromprinzips fuer waermeaustauscher, luft/wasser, luft/luft oder sinngemaess fuer andere medien
CH666538A5 (de) * 1985-05-15 1988-07-29 Sulzer Ag Waermeuebertrager mit mehreren parallelen rohren und auf diesen angebrachten rippen.
US4738225A (en) * 1987-06-03 1988-04-19 Juang Jinn C Heat transfer apparatus for water heater
JPH0258665U (fr) * 1988-10-18 1990-04-26
US5174373A (en) 1990-07-13 1992-12-29 Sanden Corporation Heat exchanger
AU663168B2 (en) * 1992-02-28 1995-09-28 Milne Jurisich Heat exchanger assembly
EP0693171B1 (fr) * 1993-03-29 1999-10-27 Melanesia International Trust Company Limited Ensemble echangeur de chaleur
DE9400687U1 (de) 1994-01-17 1995-05-18 Thermal Waerme Kaelte Klima Verdampfer für Klimaanlagen in Kraftfahrzeugen mit Mehrkammerflachrohren
JPH09138081A (ja) 1995-11-15 1997-05-27 Chubu Electric Power Co Inc 混合冷媒用熱交換器
DE19644674A1 (de) * 1996-10-28 1998-04-30 Schilling Heinz Kg Lamellenrohr-Wärmeaustauscher in Blockbauweise zur Wärmeübertragung zwischen gas-, dampfförmigen oder flüssigen Medien mit horizontalen Trennflächen
DE19719252C2 (de) * 1997-05-07 2002-10-31 Valeo Klimatech Gmbh & Co Kg Zweiflutiger und in Luftrichtung einreihiger hartverlöteter Flachrohrverdampfer für eine Kraftfahrzeugklimaanlage
DE19729239A1 (de) * 1997-07-09 1999-01-14 Behr Gmbh & Co Rohr-/Rippenblock für einen Wärmeübertrager und Herstellungsverfahren hierfür
JP2001289535A (ja) 2000-04-10 2001-10-19 Zexel Valeo Climate Control Corp 熱交換器
US20020153129A1 (en) 2000-04-25 2002-10-24 White Stephen L. Integral fin passage heat exchanger
JP4180801B2 (ja) 2001-01-11 2008-11-12 三菱電機株式会社 冷凍空調サイクル装置
US6550529B1 (en) * 2002-04-17 2003-04-22 Sunonwealth Electric Machine Industry Co., Ltd. Heatsink device
DE20302208U1 (de) * 2003-02-11 2003-06-26 Schmid Christoph Wärmeübertrager

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004068052A1 *

Also Published As

Publication number Publication date
JP2006513395A (ja) 2006-04-20
AU2003294016A1 (en) 2004-08-23
JP4092337B2 (ja) 2008-05-28
CN1745288B (zh) 2010-12-08
US20060153551A1 (en) 2006-07-13
DE10304077A1 (de) 2004-08-12
EP1588114B1 (fr) 2013-08-28
CN1745288A (zh) 2006-03-08
WO2004068052A1 (fr) 2004-08-12

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