WO2006128684A1 - Radiateur - Google Patents

Radiateur Download PDF

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Publication number
WO2006128684A1
WO2006128684A1 PCT/EP2006/005178 EP2006005178W WO2006128684A1 WO 2006128684 A1 WO2006128684 A1 WO 2006128684A1 EP 2006005178 W EP2006005178 W EP 2006005178W WO 2006128684 A1 WO2006128684 A1 WO 2006128684A1
Authority
WO
WIPO (PCT)
Prior art keywords
radiator
hollow profile
channels
hollow
front wall
Prior art date
Application number
PCT/EP2006/005178
Other languages
German (de)
English (en)
Inventor
Hans-Peter Bierbaumer
Original Assignee
Hydrogen Research Aktiengesellschaft
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 Hydrogen Research Aktiengesellschaft filed Critical Hydrogen Research Aktiengesellschaft
Priority to EP06754006A priority Critical patent/EP1888992B1/fr
Priority to DE502006003328T priority patent/DE502006003328D1/de
Publication of WO2006128684A1 publication Critical patent/WO2006128684A1/fr

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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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being attachable to the element
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0246—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid heat-exchange elements having several adjacent conduits forming a whole, e.g. blocks
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • 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
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0035—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for domestic or space heating, e.g. heating radiators

Definitions

  • the invention relates to a radiator with at least one, of a heat transfer medium flowed through hollow profile, which consists of a front wall and at least partially spaced rear wall, which are interconnected by two side walls to form a channel, and each with at least one inlet and one Drain for the heat transfer medium.
  • radiators which are mainly used for space heating, usually consist of a flat sheet metal housing, which is flowed through by warm water and whose heat radiates through a corrugated sheet-like corrugated wall of this panel radiator.
  • Such a heating element is e.g. known from DE 297 18 876 Ul.
  • the latter has a part through which a flowing, heat-transferring medium flows and a heat-dissipating part, wherein the heat-transferring part is designed to be connectable to a pipe or the like pipe leading the flow medium.
  • a flat profile containing a flow channels has clamping elements integrally formed on at least one outer surface for parts which can be connected to them as temperature-dissipating parts.
  • the radiator i. its flat profile or the lamellar inserts are made of a light metal alloy and are produced by extrusion.
  • the flat profile consists of two spaced-apart profile walls and connecting them with the flow channels limiting, approximately parallel transverse walls. In order to create the largest possible heat-transmitting surface, short rib strips are formed on the inner surfaces within the channels of this radiator. Furthermore, depending on the required performance of the space heater several of these flat profiles can be arranged in alignment with each other.
  • This object of the invention is achieved in that the distance between the front wall and the rear wall of the hollow profile is selected from a range with a lower limit of 1 mm and an upper limit of 5 mm.
  • the radiator has so much small clear width, it was surprisingly found that despite this small flow cross-section, an improved heat exchange and thus improved heating performance is obtained. The reason for this is probably to be found in the fact that due to the small flow cross-section, at least a large part of the heat transported by the heat transfer medium is transferred to the walls delimiting the flow channel, that is to say, not unnecessarily heat in the circulation, as in conventional central heating the case is being transported.
  • this radiator Due to the reduced distance between the front and rear wall of the hollow profile, not only a more compact construction of the radiator is possible and thus a less inconspicuous installation in a room to be heated, if necessary, this radiator can even be designed as a wall panel, but it is also the To achieve an advantage that it responds very quickly and thus in a very short time, the space heating is possible.
  • this rapid space heating it is possible, in particular in the case of low or low energy houses, to shorten the pumping times for the circulation of the heat transfer medium, eg of the heating water, by the more efficient heat transfer or heat exchange, and consequently in the consequence To save energy.
  • the heating times of the boiler or the heat-generating heat generator can be reduced, so that overall the operating times of the heating system can be shortened and thus the maintenance intervals are extended accordingly.
  • the distance between the front wall and the rear wall of the hollow profile is selected from a range with a lower limit of 2 mm and an upper limit of 4 mm, or according to another embodiment, this variant Distance 3 mm.
  • the front wall can be arranged with the rear wall connecting at least one further web to form at least one further channel.
  • a multi-channel system is created in the profile, whereby the flow cross-section of a single channel is further reduced and thus the heat transfer can be made more efficient and it is also possible through this training, with a corresponding connection of flow or return with only one hollow section a snake - or meandering flow through the radiator to produce.
  • the at least one web With the at least one web, the compressive strength of the hollow profile and thus the be improved mobility of the radiator.
  • This at least one web can have a wall thickness selected from a range with a lower limit of 0.35 mm and an upper limit of 1 mm. Due to this very small wall thickness of the at least one web, heat transfer into the respective laterally adjacent channels is possible, in particular in the case of meander-shaped flow guidance-in addition to the heat transfer through heat conduction into the room air-so that a homogenization of the temperature profile of the hollow profile can be achieved and thus also a correspondingly uniformed radiating surface of the radiator. This can be achieved so that the heat transfer from the "hot inlet into the" cold drain within a hollow section is made possible.
  • the at least one web can have a wall thickness selected from a range with a lower limit of 0.4 mm and an upper limit of 0.8 mm, or the wall thickness of the at least one web can be 0.5 mm be.
  • the channels are arranged directly next to one another in the hollow profile. Due to the side-by-side arrangement of the channels, these cover virtually the entire surface of the hollow profile, which is available for heat transfer and can thus be achieved with respect to this area a higher efficiency.
  • the number of channels in the hollow profile can be selected from a range with a lower limit of 15 and an upper limit of 40, or according to a further embodiment thereof with a lower limit of 20 and an upper limit of 30, in particular, the number of Channels in the hollow section 24 amount.
  • the response of the radiator can be further improved, in particular so that several channels can already be connected to the inlet, so that already at the inlet of the heat transfer medium in the radiator a correspondingly large area for heat transfer and thus a correspondingly high efficiency can be achieved ,
  • the width of the channels is selected from an area with a lower limit of 1.5 mm and an upper limit of 5 mm, or if the width of the channels is selected from a range with a lower limit of 2 mm and an upper limit of 3, 5 mm and 3 mm, respectively the width of the channels is 2.2 mm, so that due to this reduced flow cross-section virtually no "core flow" is formed which flows unused through the channels of the hollow profile.
  • the width of the channels in the direction of the front wall is smaller than the distance of the front wall of the rear wall, as can be obtained correspondingly favorable flow conditions.
  • the hollow profile may have a width selected from a range having a lower limit of 40 mm and an upper limit of 400 mm, or the width may be selected from a range having a lower limit of 80 mm and an upper limit of 250 mm , or the hollow profile may have a width of 100 mm, so that the radiator is adaptable to the desired heating power by the optional multiple arrangement of hollow sections in the radiator.
  • the front wall and / or rear wall and / or the side walls with a wall thickness, which is selected from a range with a lower limit of 0.5 mm and an upper limit of 1.5 mm.
  • the wall thickness of the front wall and / or rear wall and / or the side walls from a range with a lower limit of 0.75 mm and an upper limit of 1, 2 mm or the wall thickness 0.9 mm.
  • the heating power it is possible to vary the heating power to provide a plurality of hollow sections to form a channel system via manifolds fluidly connected to each other in the radiator.
  • the flow connection can be made via the opposite open profile ends of the hollow sections, so that therefore additional Built-in hollow profile can be dispensed with.
  • the flow connection can be designed so that the heat transfer medium flows through the channel system meandering, so that this travels the longest possible path through the radiator before it leaves this again through the flow and thus a correspondingly long period for heat exchange is available.
  • front wall and the rear wall are arranged at least approximately parallel to one another, it is possible to form the channels at least approximately with the same flow cross section.
  • the cross-section of the channels may be rectangular, square, round, trapezoidal, rhomboid, diamond-shaped or triangular, with mixed forms within a radiator are also possible, for example, to influence the flow behavior positively or to keep power losses due to the resulting pressure gradient as low as possible ,
  • the hollow profile itself can be extruded, since it can be used on a standardized method for the production of hollow sections and the manufacturing costs can be reduced by a manageable mass production. Moreover, it is with the
  • the hollow profile has been subjected to deformation after extrusion to reduce the distance between the front and rear walls, in particular cold working, e.g. Pressing or rolling, since this means that the extruded hollow profiles are in principle of larger flow cross-section, i. greater distance between the front and rear walls and can be produced as a result of higher dimensional accuracy.
  • said manifolds may be connected by at least one bend with the inlet and outlet, whereby the inlet or outlet in the rear region of the Schugropers, ie invisible from the visible side of the radiator, can be arranged.
  • the hollow profile is formed of aluminum or an aluminum alloy, since these materials are known for their high conductivity and thus the efficiency of the radiator can be further improved.
  • FIG. 1 shows a first embodiment of a hollow profile for a radiator according to the invention in an oblique view.
  • FIG. 2 shows a section of a variant of the hollow profile in an oblique view with a plurality of channels.
  • Fig. 3 is a hollow profile in plan view with diamond-shaped channels
  • Fig. 4 shows the arrangement of four hollow sections in a radiator
  • FIG. 5 shows a hollow profile in plan view with lamellae arranged thereon for heat transfer
  • FIG. 6 the detail of a hollow profile with lateral collecting channel cut in side view
  • Figure 7 shows the integration of several hollow sections in a manifold.
  • FIG. 8 shows an embodiment variant for the integration of the hollow profiles into a collecting line
  • FIG. 9 shows a further embodiment variant for incorporating the hollow profiles in a collecting line
  • FIG. 10 shows a further embodiment variant for incorporating the hollow profiles into a collecting line
  • FIG. 11 shows an embodiment variant of the radiator with a schematically illustrated meander-shaped flow pattern of the heat transfer medium
  • FIG. 13 an embodiment variant of the hollow profile in front view
  • Fig. 14 shows a variant of the hollow profile in front view.
  • FIG. 1 shows a hollow profile 1 for a radiator 2 (see, for example, Fig. 7), which comprises a front wall 3, a rear wall 4 and two side walls 5, 6.
  • a radiator 2 see, for example, Fig. 7
  • the front wall 3 and the rear wall 4 are of planar design and at least approximately parallel to one another.
  • the two side walls 5, 6 are formed at least approximately parallel to each other and planar.
  • the inlet 7 and the outlet 8 can be arranged in only one of the side wall 5, 6 or it is also possible to arrange this inlet 7 and / or outlet 8 in the front wall 3 and / or rear wall 4 as needed.
  • the hollow profile 1 is provided with only one channel 9, in which the heat transfer medium of this hollow profile 1 flows through, while the heat, which in a heat source, e.g. a burner boiler according to the prior art, is transmitted to the front wall 3 and / or rear wall 4 and / or the side walls 5,6,
  • a heat source e.g. a burner boiler according to the prior art
  • the hollow profile 1 is preferably made of a material, in particular metal, formed with high thermal conductivity, in particular it consists of aluminum or an aluminum alloy.
  • the hollow profile can thus be made very light, for example, have a weight which is selected from a range with a lower limit of 0.5 kg / m and an upper limit of 0.75 kg / m, for example, the weight 0.66 kg / m.
  • radiator 2 By using an aluminum material for the radiator 2, this is relatively easy. In addition, it has a fast response, so that after a short time a correspondingly large amount of heat has been transferred to the room air. Furthermore, it is possible with the radiator 2 according to the invention, in particular since its clear width, so the flow cross-section, is relatively low to heat the heat transfer medium to a higher temperature, since the registered heat is transferred very quickly into the aluminum material and thus introduced into the room air , Due to this rapid response, it is possible to dispense with conventional lamellae known from the prior art for enlarging the heat-transferring surface, although these can of course be arranged.
  • a distance 10, ie in this case the clear width of the channel 9, is relatively small, in particular selected from a range with a lower limit of 1 mm and an upper limit of 5 mm. It is thus achieved a very small flow cross-section for the heat transfer medium, so that its heat evenly on the channel 9 surrounding the front wall 3, rear wall 4 and sides walls 5, 6 transmits and in the heat transfer medium itself substantially inside no central Flow is formed, in which the heat is practically unused by the heat transfer medium in circulation. To avoid this, theoretically there is the possibility of making the radiator 2 over a large area, so that therefore a long flow path through the channels 9 of the radiator 2 must be covered and thus the heat can be transferred from these central areas to the corresponding walls.
  • radiator 2 In the case of the radiator 2 according to the invention, this is not necessary, so that this radiator 2 can be made relatively compact and thus at least approximately constant heating power compared to radiators from the prior art, the formation of a radiator 2 is possible in a room practically in the background occurs.
  • this hollow section 1 is produced by extrusion of aluminum or an aluminum alloy. This has the advantage that it can be used to produce a hollow profile 1 with very thin walls, so that in turn the heat transfer, i. the heat exchange from the heat transfer medium to the ambient air surrounding the radiator 2, is made possible.
  • the front wall 3 and / or rear wall 4 and / or the two side walls 5, 6 has a wall thickness 11, which is selected from a range with a lower limit of 0.5 mm and an upper limit of 1, 5 mm.
  • this wall thickness 11 can be further reduced, in particular be selected from a range with a lower limit of 0.75 mm and an upper limit of 1, 2 mm.
  • the wall thickness 11 for the front wall 3 and / or the rear wall 4 and / or the two side walls 5, 6 preferably has a wall thickness of 0.9 mm.
  • the hollow profile 1 should be self-supporting, that is to say should have a certain strength, a reduction of the wall thickness 11 below 0.5 mm is not provided.
  • the strength of the hollow section 1 to this extent not be required, for example, when the hollow section 1, a kind of cage, for example in the form of a grid, constructed, which takes on a strength by the carrying function and on the other hand, the hollow section 1 against the outside Shock and thus deformation of the same protects, of course, in the context of the invention, the wall thickness 11 be less than 0.5 mm.
  • a further improvement of the heating capacity, ie the heat transfer, to achieve by further reducing this distance 10 takes a value from a range with a lower limit of 2 mm and a upper limit of 4 mm.
  • this distance 10 between the front wall 3 and the rear wall 4 3 mm is a value from a range with a lower limit of 2 mm and a upper limit of 4 mm.
  • the hollow profile 1 it is possible to produce the hollow profile 1 with a greater distance between the front wall 3 and the rear wall 4 than 5 mm. In this case, or to further reduce the distance 10, it is possible, the hollow profile 1 after the extrusion of a deformation, in particular a cold deformation, e.g. by pressing or rolling, to submit.
  • a deformation in particular a cold deformation, e.g. by pressing or rolling
  • the minimum distance is 1 mm. Below lying distances, ie clear widths of the hollow section 1, however, can be used when the pump power for the circulation of the heat carrier is correspondingly high.
  • the metal from which the hollow profile 1 is produced is preferably made of an aluminum material, ie aluminum or an aluminum alloy. These materials are particularly suitable for producing hollow sections 1 by extrusion or cold forming.
  • aluminum has the advantage of being more cost effective and substantially more corrosion resistant to iron than copper, which is commonly used in radiator construction.
  • Fig. 2 shows a variant of the hollow profile 1 is shown.
  • the channel 9 of the hollow profile 1 according to FIG. 1 is divided into a plurality of individual channels 9, so that therefore at least two channels 9 are present in the hollow profile 1.
  • This is achieved by extending between the side walls 5, 6 in the direction of these side walls 5, 6 and connecting the front wall 3 with the rear wall 4, at least one web 12 is arranged.
  • this web 12 is also produced simultaneously with the hollow section 1 by extrusion. Since the at least one web 12 has only a limited support function, it is possible to perform this with a smaller wall thickness 13, which may be selected from a Range with a lower limit of 0.35 mm and an upper limit of 1 mm.
  • this wall thickness 13 is selected from a range with a lower limit of 0.4 mm and an upper limit of 0.8 mm or this wall thickness can be 0.5 mm.
  • this at least one web 12 it is possible to divide the heat carrier to a plurality of channels 9, so that the flow cross-section is further reduced and thus heat transfer via these webs 12, which are connected to the front wall 3 and rear wall 4 and thus to initiate this heat in these channels 9, to allow.
  • the heat transfer medium that is to say the heating water, serpentine or meandering, so that, for example, a first channel 9 for the upward flow of the heat transfer medium and a further channel 9 for the downward flow the heat transfer medium is used.
  • This extends the flow path of the heat transfer medium in the hollow profile 1 and is therefore also a longer period of time for the heat exchange available.
  • the webs 12 thus increase the heat transfer surfaces and thus improve the efficiency. For this it is thus possible to give the hollow section 1 a higher pressure resistance and the radiator 2 with a higher operating pressure, which can reach up to several bar operate.
  • the two side walls 5, 6 need not be flat, but for example, may also have a curvature.
  • the front wall 3 and / or the rear wall 4 have such a curvature, so that, for example, the maximum distance of 5 mm between the front wall 3 and the rear wall 4 is achieved only in the central region of the hollow section 1 and in the two side areas of the two side walls 5, 6, the channels 9 lower light
  • the variation of the size of the flow cross-section within a hollow section 1 or the Radiator 2 is generally for all embodiments of the invention, a way to influence the flow resistance.
  • the hollow profile 1 provided for a radiator 2, in particular a flat radiator, preferably has a width 14 selected from a range with a lower limit of 40 mm and an upper limit of 400 mm. This makes it possible to provide a plurality of channels 9 in the hollow section 1 - if equal to this width 14 of the hollow section 1 is also appropriate if only one channel 9 is provided in this - so as to pretend a corresponding flow of the heat transfer medium in the hollow section 1. However, this width 14 may be further selected from a range having a lower limit of 80 mm and an upper limit of 250 mm and 100 mm, respectively.
  • only one channel 9 can be formed in the hollow profile 1.
  • the adjacent channels 9 cover virtually the entire radiator surface or Hohlprof ⁇ l Chemistry. This is a very high efficiency of the radiator 2 can be achieved.
  • a width 15 of the channels 9, so the lateral distance between the webs 12 is selected, from a range with a lower limit of 1.5 mm and an upper limit of , 5 mm.
  • an improved efficiency can be achieved, namely in which the ratio of the cross-sectional area of the channel 9 in relation to the heat transfer surface on the front wall 3, the rear wall 4 and the two side walls 5, 6 and the webs 12 is correspondingly low adjustable ,
  • the width 15 of the channels 9 from a range with a lower limit of 2 mm and an upper limit of 3 mm and the width 15 of the channels 9 on the order of 2.2 mm choose.
  • the cross-section of the channels 12 can be chosen arbitrarily, that is, for example, rectangular, square, round, trapezoidal, rhomboid, diamond-shaped or triangular and is to this end in Fig. 3, to illustrate this, hinted another embodiment of the hollow section 1 in plan view.
  • This hollow profile 1 consists essentially of a Sequence of erected squares, in particular squares, wherein the connection of the individual squares takes place via the corners, so that therefore the cross section of the channels 9 is also quadrangular or square.
  • the front wall 3 and the rear wall 4 are not formed by planar walls, but instead have a zig-zag-shaped profile when viewed in cross-section.
  • the distance 10 of the front wall 3 of the rear wall 4 of that distance 10 which is formed between two opposite corners. This distance is reduced after the channels 9 are connected to each other via the corners to zero and then increase again to the maximum value. In this sense, the definition of this distance 10 is to be understood in the context of the invention.
  • Dashed line is indicated in Fig. 3 that also in this variant of the hollow profile 1, the channels just described 9 outside of a front wall 3, a rear wall 4 and the side walls 5, 6 may be limited, in the context of the embodiment of FIG. 1.
  • Vorzugs - are the previously described the distance 10 as defining described opposing vertices connected to these walls.
  • this structure can also be produced by extrusion. It is also conceivable that these corners are connected via, for example, welds with the individual walls. It is thus possible, in addition to these square or diamond-shaped channels 9 in the edge regions of the hollow profile 1, to form further channels 9 with a triangular cross section, so that this hollow profile 1 has a large number of individual channels.
  • the individual channels 9 are in fluid communication with each other, wherein the individual hollow sections 1 can be connected to each other, for example via pipes 16.
  • the two broad sides forming hollow sections 1 have more than one channel 9 or conversely, it is also possible that the longitudinal sides forming hollow sections 1, i. at least one of which has only one channel 9.
  • the inlet 7 and the outlet 8 is arranged for the heat transfer medium.
  • these are located on the rear wall of the radiator 2, so as to allow an externally at least approximately invisible supply line of the heat transfer medium.
  • the radiator 2 may comprise only a hollow profile 1. 5 is merely intended to illustrate that, of course, in the case of the hollow profile 1 according to the invention, ie a radiator 2 formed therefrom, according to the state of the art, so-called lamellae 17 for enlarging the heat-emitting surface on one of the walls of the hollow profile 1 , so for example, the rear wall 4 to arrange. It is also a centric arrangement of the hollow section 1 in the radiator 2 is possible, so that therefore the hollow section 1 viewed in cross-section is surrounded on all sides by such fins 17. In this case, it is advantageous if the radiator 2 has at least one outer lining element in order to avoid direct inspection of the inner structure, in particular the lamellae 17, provided that they have a visually disturbing effect.
  • a collecting line 18 for example with a rectangular cross-section.
  • This bus 18, i. the cross-sectional widening in this area can be produced in such a way that one of the two opposing walls, that is to say, for example, the rear wall 4, is produced with a greater length than the front wall 3.
  • the end portions of the two walls, i. the front wall 3 and the rear wall 4 can be welded together to produce the necessary tightness, as indicated in Fig. 6.
  • manifolds 18, which connect individual channels with each other are generated, in which, for example, the heat transfer medium is supplied or which are also used in a serpentine or meandering course of the heat transfer medium within a hollow section 1, the corresponding Studentsertrittssch of to create a channel 9 in another channel 9.
  • the feed 7 or the outlet 8 of the heat transfer medium can also be provided on these collecting lines 18.
  • the manifolds 18 may be formed extending transversely to the channels 9.
  • FIGS. 7 to 10 show a wide variety of possible connections of a plurality of hollow profiles 1 in a supply line 19 and discharge line 20 for the heat transfer medium.
  • FIG. 7 it is possible to provide corresponding slot-shaped recesses in the feed line 19 and the discharge line 20 into which or to which the hollow sections 1 are connected, for example welded to them, in order to establish the flow connection.
  • the hollow sections 1 are aligned at least approximately parallel to the feed line 19 and the discharge line 20.
  • FIG. 8 shows, to equip the open ends of the hollow profile 1 with additional connecting devices 21, which may be hood-shaped, for example. These connecting devices 21 can in turn be welded to the hollow profiles 1 on the one hand and to the collecting line 18 or the supply line 19 on the other hand.
  • the execution of a radiator 2 of Fig. 8 the hollow sections 1 - although only three hollow sections 1 are shown, it is of course possible to arrange more or less of these hollow sections 1 in the radiator 2 - in contrast to the embodiment of FIG. 7 not aligned at least approximately parallel to the feed line 19 and the drain line 20, but at least approximately perpendicular thereto.
  • a distance 22 between the individual hollow profiles 1 can be chosen so that between the hollow profiles 1 a kind of forced convection is formed, so which these hollow sections 1 are flowed around by the surrounding room air and thus a better heat transfer through the inflowing from below cooler air and thus An increase in the efficiency is possible.
  • these hollow sections 1 rotatable in the supply line 19 and
  • drain line 20 so that these hollow sections 1 can be rotated in the manner of a slat curtain from an approximately parallel orientation in an approximately vertical orientation and thus the convection between the hollow sections 1 can be varied accordingly.
  • FIG. 9 shows a variant in which, in contrast to the preceding FIGS. 7 and 8, the feed line 19 and the discharge line 20 are arranged on the same side of the hollow sections 1, for example at the top.
  • the hollow profiles 1 can be used for additional sam- Mels 18 to the flow connection in the supply line 19 and the drain line 20 to be integrated.
  • this manifold 18 can be arranged at the open end of each hollow section 1, wherein preferably the integration into the drain line 20 via a pipe bend, not shown, which predetermines the flow direction of the heat transfer medium.
  • Such a pipe bend can also be provided in the region of the feed line 19.
  • the other open ends of the hollow profile 1 must of course be closed in this embodiment. This is done for example by welding with a cover element.
  • a manifold 18 should also be provided in the lower area. Also in this case, a meandering flow pattern of the heat transfer medium within a hollow profile 1 is achieved.
  • Fig. 10 shows a variant in which the integration of the hollow sections 1 in the supply line 19 and the drain line 20 of the radiator 2 via simple pipe connections according to the prior art is performed.
  • FIG. 11 shows an alternative embodiment of the radiator 2, again with several hollow profiles 1. These are flowed through in a serpentine manner according to arrow 23, wherein within the hollow profile 1 the heat transfer medium in the channels 9 (not shown) has the same flow direction.
  • both the inlet 7 and the outlet 8 are provided in the lower region of the radiator 2, so that in other words, the radiator 2 stands on the inlet 7 or outlet 8.
  • Fig. 12 shows a variant of the hollow profile 1 in front view.
  • the rear wall 4 is made flat, whereas the front wall 3 is formed corrugated in the manner of a sawtooth.
  • the corrugation extends into the channels 9, so that they have a substantially pentagonal cross-section.
  • the corrugation can be formed exclusively on the outer surface of the front wall 3, so that the channels 9 again have a substantially quadrangular cross section.
  • FIG. 14 also shows an alternative embodiment of the hollow profile 1, in which both the front wall 3 and the rear wall 4 have this corrugation, in which case the corrugation does not extend into the channels 9, ie they have a substantially quadrangular cross section ,
  • the corrugation according to FIG. 12 wherein the front wall 3 and / or the rear wall 4 can be provided with it.
  • the front wall 3 and the rear wall 4 may also have a different corrugation or, in general, a different surface structuring.
  • the corrugation in these variants can also be designed so that not in the region of each web 12 a wave crest is arranged, but that the wave troughs extend over at least two adjacent channels.
  • the corrugation is not provided with curves, but that the wave crests are connected with straight lines, or are hybrids of curves and straight lines possible.
  • the radius of the rounding can also be adapted to the respective requirements, or a rounding can have several different radii.
  • the width 14 of the hollow profile 1 according to FIG. 12 is, for example, 120 mm.
  • the width 15 is 4.3 mm.
  • the wave crests can, for example, rise by 1.4 mm over the wave troughs, whereby a variation of wave height in the range between 0.75 mm and 3 mm is possible here.
  • the exemplary embodiments show possible embodiments of the radiator 2 according to the invention or of the hollow profile 1 according to the invention, it being noted at this point that the invention is not limited to the specifically illustrated embodiments thereof, but rather various combinations of the individual embodiments are possible with each other and this possibility of variation due to the teaching on technical action by objective invention lies in the ability of those skilled in this technical field. So are all conceivable embodiments, which are possible by combinations of individual details of the illustrated and described embodiment variant, includes the scope of protection.

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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)
  • Domestic Hot-Water Supply Systems And Details Of Heating Systems (AREA)
  • Surgical Instruments (AREA)
  • Central Heating Systems (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)

Abstract

L'invention concerne un radiateur (2) comprenant au moins un profil creux (1) qui est traversé par un milieu caloporteur et qui est constitué d'une paroi avant (3) et d'une paroi arrière (4) placée au moins partiellement à une certaine distance (10) de la paroi avant, la paroi avant et la paroi arrière étant reliées l'une à l'autre par deux parois latérales (5, 6) avec formation d'au moins un conduit (9). Le radiateur selon l'invention comprend également au moins une amenée (7) et une évacuation (8) pour le milieu caloporteur et, éventuellement, des lamelles (12) placées sur le profil creux (1) et servant à améliorer la dissipation de la chaleur. La distance maximale (10) entre la paroi avant (3) et la paroi arrière (4) est sélectionnée dans une plage ayant 1 mm comme limite inférieure et 5 mm comme limite supérieure.
PCT/EP2006/005178 2005-06-01 2006-05-31 Radiateur WO2006128684A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP06754006A EP1888992B1 (fr) 2005-06-01 2006-05-31 Radiateur
DE502006003328T DE502006003328D1 (de) 2005-06-01 2006-05-31 Heizkörper

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0093805A AT501943A1 (de) 2005-06-01 2005-06-01 Heizkörper
ATA938/2005 2005-06-01

Publications (1)

Publication Number Publication Date
WO2006128684A1 true WO2006128684A1 (fr) 2006-12-07

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/005178 WO2006128684A1 (fr) 2005-06-01 2006-05-31 Radiateur

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Country Link
EP (1) EP1888992B1 (fr)
AT (2) AT501943A1 (fr)
DE (1) DE502006003328D1 (fr)
RU (1) RU2007149516A (fr)
WO (1) WO2006128684A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1983272A1 (fr) * 2007-04-18 2008-10-22 Aic S.A. Faisceau d'échangeur thermique à combustible

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU184729U1 (ru) * 2016-12-02 2018-11-07 Юрий Константинович Морозов Радиатор для охлаждения электронных устройств

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03102193A (ja) * 1989-09-13 1991-04-26 Showa Alum Corp 凝縮器
JP2000304472A (ja) * 1999-04-23 2000-11-02 Calsonic Kansei Corp 冷凍サイクル用熱交換器
EP1058070A2 (fr) * 1999-06-04 2000-12-06 Denso Corporation Evaporateur de réfrigérant
US20010004935A1 (en) * 1999-12-09 2001-06-28 Ryouichi Sanada Refrigerant condenser used for automotive air conditioner
EP1342970A1 (fr) * 2000-11-24 2003-09-10 Showa Denko K.K. Tube d'echangeur de chaleur et echangeur de chaleur
WO2004031676A1 (fr) * 2002-10-02 2004-04-15 Showa Denko K.K. Tube echangeur de chaleur et echangeur de chaleur

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Publication number Priority date Publication date Assignee Title
JPS59129392A (ja) * 1983-01-10 1984-07-25 Nippon Denso Co Ltd 熱交換器
GB2344643B (en) * 1998-12-07 2002-06-26 Serck Heat Transfer Ltd Heat exchanger core connection
US6973965B2 (en) * 2002-12-11 2005-12-13 Modine Manufacturing Company Heat-exchanger assembly with wedge-shaped tubes with balanced coolant flow

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03102193A (ja) * 1989-09-13 1991-04-26 Showa Alum Corp 凝縮器
JP2000304472A (ja) * 1999-04-23 2000-11-02 Calsonic Kansei Corp 冷凍サイクル用熱交換器
EP1058070A2 (fr) * 1999-06-04 2000-12-06 Denso Corporation Evaporateur de réfrigérant
US20010004935A1 (en) * 1999-12-09 2001-06-28 Ryouichi Sanada Refrigerant condenser used for automotive air conditioner
EP1342970A1 (fr) * 2000-11-24 2003-09-10 Showa Denko K.K. Tube d'echangeur de chaleur et echangeur de chaleur
WO2004031676A1 (fr) * 2002-10-02 2004-04-15 Showa Denko K.K. Tube echangeur de chaleur et echangeur de chaleur

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 015, no. 286 (M - 1138) 19 July 1991 (1991-07-19) *
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 14 5 March 2001 (2001-03-05) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1983272A1 (fr) * 2007-04-18 2008-10-22 Aic S.A. Faisceau d'échangeur thermique à combustible

Also Published As

Publication number Publication date
ATE427467T1 (de) 2009-04-15
AT501943A1 (de) 2006-12-15
DE502006003328D1 (de) 2009-05-14
RU2007149516A (ru) 2009-07-20
EP1888992A1 (fr) 2008-02-20
EP1888992B1 (fr) 2009-04-01

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