EP1888992B1 - Radiateur - Google Patents

Radiateur Download PDF

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Publication number
EP1888992B1
EP1888992B1 EP06754006A EP06754006A EP1888992B1 EP 1888992 B1 EP1888992 B1 EP 1888992B1 EP 06754006 A EP06754006 A EP 06754006A EP 06754006 A EP06754006 A EP 06754006A EP 1888992 B1 EP1888992 B1 EP 1888992B1
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EP
European Patent Office
Prior art keywords
heating body
hollow
front wall
rear wall
radiator
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.)
Active
Application number
EP06754006A
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German (de)
English (en)
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EP1888992A1 (fr
Inventor
Hans-Peter Bierbaumer
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Hydrogen Research AG
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Hydrogen Research AG
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Priority to AT06754006T priority Critical patent/ATE427467T1/de
Publication of EP1888992A1 publication Critical patent/EP1888992A1/fr
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Publication of EP1888992B1 publication Critical patent/EP1888992B1/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 as described in the preamble of claim 1.
  • Known radiator which are mainly used for space heating, usually consist of a flat sheet metal housing that is traversed by warm water and whose heat radiates through a corrugated sheet-like corrugated wall of this panel radiator.
  • Such Thompsonköper is eg from the EP-A-1058070 , or the DE 297 18 876 U1 known.
  • This has a part through which a flowing, heat-transferring medium flows and a heat-dissipating part, wherein the heat-transferring part is connectable to a pipe or the like leading to 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 ie its flat profile or the lamellar inserts, consist 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 heat is transferred to the walls bounding the flow channel, so so simplified, not unnecessarily heat in the circuit, as is the case with conventional central heating is, is transported.
  • radiator Due to the reduced distance between the front and rear walls of the hollow profile is not only a more compact design 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 advantage to achieve that it responds very quickly and thus in a very short time, the space heating is possible.
  • 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 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 can also the compressive strength of the hollow profile and thus the stability of the radiator can be improved.
  • 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 optionally possible, in particular in meandering flow guidance - in addition to the heat transfer by 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 formed by this reduced flow cross section virtually no "core flow", 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 is the back wall and the side walls to form a wall thickness, which is selected from an area 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.
  • the extrusion process in a simple manner, the hollow profile according to the invention with the small distance of the front wall of the rear wall with a correspondingly high dimensional accuracy and without much Nachbearbeitungsaufwand produce.
  • By extrusion it is also possible to easily produce the hollow sections with virtually any length.
  • 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, as this allows the extruded hollow profiles in principle with a 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 is a hollow section 1 for a radiator 2 (see, eg Fig. 7 ), which comprises a front wall 3, a rear wall 4 and two side walls 5, 6.
  • the front wall 3 and the rear wall 4 are planar in this embodiment of the hollow profile 1 and at least approximately parallel to each other.
  • 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 , By this rapid response, it is possible to dispense with conventional, known from the prior art slats to increase the heat-transmitting 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 this evenly transfers its heat to the surrounding the channel 9 front wall 3, rear wall 4 and side walls 5, 6 and thereby 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 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 an upper Border 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 an upper Border 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 a variant of the hollow profile 1 is shown.
  • the channel 9 of the hollow profile 1 is after Fig. 1 split, in several individual channels 9, so that in the hollow section 1 at least two channels 9 are present.
  • 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 ie for example the heating water, serpentine or meandering to guide, so so for example, a first channel 9 for the upward flow of the heat transfer medium and another channel 9 for the downward flow of 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 may for example 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 have smaller clear width.
  • an increase in the flow cross-section in the center region of the hollow profile 1 can be deliberately formed in order to vary, for example, the flow resistance within the hollow profile 1 or to design the flow profile such that the flow resistance over the hollow profile 1 is at least approximately constant within narrow limits.
  • 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 hollow profile surface. This is a very high efficiency of the radiator 2 can be achieved.
  • a width 15 of the channels 9, ie 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 3 , 5 mm.
  • 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 heat-radiating surfaces are either the front wall 3 or the rear wall 4 or the side walls 5, 6, ie those walls which communicate with the ambient air, if the width 15 of the channels 9 is smaller, as the distance 10 of the front wall 3 of the rear wall 4, since ultimately the transmitted heat in the webs 12 must also be forwarded in these outer walls.
  • 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 for this purpose in Fig. 3 in order to clarify this, hinted another variant 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 in this embodiment of the hollow profile 1 by planar walls, but have this in cross-section, zigzag-shaped course.
  • 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.
  • Fig. 3 Dashed is in Fig. 3 indicated that in this variant of the hollow section 1, the channels 9 just described outside of a front wall 3, a rear wall 4 and the side walls 5, 6 may be limited, according to the embodiment according to Fig. 1 , Preferably, 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 rhombic channels 9 in the edge regions of the hollow section 1 further channels 9 form with triangular cross-section, so that this hollow section 1 has a plurality of individual channels.
  • the still relatively hot heat transfer medium flows in one direction and flows in the outer channels 9 with triangular cross-sections already cooled heat transfer medium against the still hot heat transfer medium, so again in turn a serpentine or meandering flow is achieved within a hollow section 1.
  • This is the heat transfer from the hot heat transfer medium on the one hand in the walls of the hollow section 1 and on the other hand in the already cooled heat transfer medium in the triangular channels 9, so that heat can still be delivered to the environment via this detour.
  • This cross-sectional shape has a particularly high stability and is therefore also suitable for higher operating pressures of a heating system.
  • Fig. 4 shows the arrangement of four hollow sections 1 for forming a radiator 2.
  • 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 vice versa is possible that the longitudinal sides forming hollow sections 1, ie 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.
  • FIG. 4 This arrangement of several hollow sections 1 after Fig. 4 represents only one of the possible embodiments and can also be arranged more than four or less than four hollow sections 1 in the radiator 2. In extreme cases, the radiator 2 may comprise only a hollow profile 1.
  • Fig. 5 should only be clarified that it is of course also in the hollow section 1 according to the invention, ie a radiator formed therefrom, according to the prior art, so-called fins 17 to increase the heat-emitting surface on one of the walls of the hollow section 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 manifold 18, for example with a rectangular cross-section.
  • This manifold 18, ie the cross-sectional widening in this area can be made such that one of the two opposite walls, so for example the rear wall 4, is made with a greater length than the front wall 3.
  • the front wall 3 protruding part of the rear wall 4 can be bent several times, so that not only the channel 9 and the channels 9 thereof are covered, but laterally even this bus 18 is formed.
  • the end regions of the two walls, ie the front wall 3 and the rear wall 4 can be welded together to produce the necessary tightness, as shown in FIG Fig. 6 is indicated.
  • 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.
  • manifolds 18 and the inlet 7 and the drain 8 of the heat transfer medium are provided.
  • the manifolds 18 may be formed extending transversely to the channels 9.
  • Fig. 7 to 10 show various integration possibilities of several hollow sections 1 in a supply line 19 and drain line 20 for the heat transfer medium.
  • Fig. 7 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 these in order to produce 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 represents to equip the open ends of the hollow section 1 with additional connecting means 21, which may be, for example, hood-shaped. 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 after Fig. 8 are 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 according to Fig. 7 not aligned at least approximately parallel to the feed line 19 and the discharge 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 rotatably in the inlet line 19 and drain line 20, so that these hollow sections 1 can be rotated in the manner of a slatted curtain from an approximately parallel orientation in an approximately vertical orientation and thus varies the convection between the hollow sections 1 accordingly can be.
  • Fig. 9 shows a variant in which, in contrast to the preceding FIGS. 7 and 8 the supply line 19 and the drain line 20 on the same side of the hollow sections 1, for example, above, are arranged.
  • the hollow sections 1 can thereby via additional manifolds 18 be integrated for flow connection in the supply line 19 and the drain line 20.
  • 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 feed 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 a variant of the radiator 2, again with several hollow profiles 1. These are traversed serpentine as shown by 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 section 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 may be formed exclusively on the outer surface of the front wall 3, so that the channels 9 in turn have a substantially quadrangular cross-section.
  • FIG. 14 Yet another variant 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, so they have a substantially quadrangular cross-section.
  • 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 be adapted to the respective requirements, or may have a rounding several different radii.
  • the width 14 of the hollow profile 1 after 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.

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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)
  • Steam Or Hot-Water Central Heating Systems (AREA)
  • Central Heating Systems (AREA)
  • Surgical Instruments (AREA)

Claims (15)

  1. Radiateur (2) pour le chauffage d'une pièce avec au moins un profilé creux (1) traversé par un milieu caloporteur, qui est constitué d'une paroi avant (3) et d'une paroi arrière (4) disposée au moins partiellement à un écart (10), qui sont reliées l'une à l'autre par deux parois latérales (5, 6) en formant au moins un canal (9), et avec respectivement au moins un afflux (7) et une évacuation (8) pour le milieu caloporteur et le cas échéant des lamelles (12) disposées au profilé creux (1) pour améliorer l'évacuation de la chaleur, caractérisé en ce que l'écart maximal (10) entre la paroi avant (3) et la paroi arrière (4) est sélectionné dans une plage ayant une limite inférieure de 1mm et une limite supérieure de 5mm, et en ce que la paroi avant (3) et la paroi arrière (4) et les parois latérales (5, 6) possèdent une épaisseur de paroi (11), sélectionnée dans une plage avec une limite inférieure de 0,5mm et une limite supérieure de 1,5mm.
  2. Radiateur (2) selon la revendication 1, caractérisé en ce qu'il est disposé entre les parois latérales (5, 6), en reliant la paroi avant (3) à la paroi arrière (4), au moins une baguette (12) en formant au moins un autre canal (9).
  3. Radiateur (2) selon la revendication 2, caractérisé en ce qu'au moins une baguette précitée (12) présente une épaisseur de paroi (13), sélectionnée dans une plage avec une limite inférieure de 0,35mm et une limite supérieure de 1,0mm.
  4. Radiateur (2) selon l'une des revendications 2 ou 3, caractérisé en ce que les canaux (9) dans le profilé creux (1) sont disposés d'une manière directement avoisinante.
  5. Radiateur (2) selon l'une des revendications 2 à 4, caractérisé en ce que le nombre des canaux (9) dans le profilé creux (1) est sélectionné dans une plage avec une limite inférieure de 15 et une limite supérieure de 40.
  6. Radiateur (2) selon l'une des revendications précédentes, caractérisé en ce qu'une largeur (15) des canaux (9) est sélectionnée dans une plage avec une limite inférieure de 1,5mm et une limite supérieure de 5mm.
  7. Radiateur (2) selon l'une des revendications précédentes, caractérisé en ce qu'une largeur (15) des canaux (9) dans la direction de la paroi avant (3) est plus petite que l'écart (10) de la paroi avant (3) de la paroi arrière (4).
  8. Radiateur (2) selon l'une des revendications précédentes, caractérisé en ce que le profilé creux (1) présente une largeur (15), sélectionnée dans une plage avec une limite inférieure de 40mm et une limite supérieure de 400mm.
  9. Radiateur (2) selon l'une des revendications précédentes, caractérisé en ce que plusieurs profilés creux (1) sont reliés quant à l'écoulement les uns aux autres par des conduites de collecte (18) en réalisant un système de canaux.
  10. Radiateur (2) selon la revendication 9, caractérisé en ce que la liaison d'écoulement est réalisée par des extrémités de profilé ouvertes opposées les unes aux autres des profilés creux (1).
  11. Radiateur (2) selon la revendication 9 ou 10, caractérisé en ce que les profilés creux (1) sont reliés quant à l'écoulement de telle sorte les uns aux autres que le milieu caloporteur s'écoule en forme de méandre à travers le système de canaux.
  12. Radiateur (2) selon l'une des revendications précédentes, caractérisé en ce que le profilé creux (1) est extrudé.
  13. Radiateur (2) selon la revendication 12, caractérisé en ce que le profilé creux (1), après l'extrusion, afin de réduire l'écart (10) entre la paroi avant (3) et la paroi arrière (4), est soumis à une déformation.
  14. Radiateur (2) selon l'une des revendications 9 à 13, caractérisé en ce que respectivement une conduite de collecte (18) est reliée par au moins un coude à l'afflux respectivement à l'écoulement.
  15. Radiateur (2) selon l'une des revendications précédentes, caractérisé en ce qu'au moins des profilés creux individuels (1) sont disposés au moins approximativement perpendiculairement sur un côté frontal du radiateur (2)
EP06754006A 2005-06-01 2006-05-31 Radiateur Active EP1888992B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT06754006T ATE427467T1 (de) 2005-06-01 2006-05-31 Heizkírper

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0093805A AT501943A1 (de) 2005-06-01 2005-06-01 Heizkörper
PCT/EP2006/005178 WO2006128684A1 (fr) 2005-06-01 2006-05-31 Radiateur

Publications (2)

Publication Number Publication Date
EP1888992A1 EP1888992A1 (fr) 2008-02-20
EP1888992B1 true EP1888992B1 (fr) 2009-04-01

Family

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EP06754006A Active EP1888992B1 (fr) 2005-06-01 2006-05-31 Radiateur

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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
RU184729U1 (ru) * 2016-12-02 2018-11-07 Юрий Константинович Морозов Радиатор для охлаждения электронных устройств

Families Citing this family (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

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59129392A (ja) * 1983-01-10 1984-07-25 Nippon Denso Co Ltd 熱交換器
JPH03102193A (ja) * 1989-09-13 1991-04-26 Showa Alum Corp 凝縮器
GB2344643B (en) * 1998-12-07 2002-06-26 Serck Heat Transfer Ltd Heat exchanger core connection
JP2000304472A (ja) * 1999-04-23 2000-11-02 Calsonic Kansei Corp 冷凍サイクル用熱交換器
EP1058070A3 (fr) * 1999-06-04 2002-07-31 Denso Corporation Evaporateur de réfrigérant
JP2001165532A (ja) * 1999-12-09 2001-06-22 Denso Corp 冷媒凝縮器
EP1342970A4 (fr) * 2000-11-24 2006-06-07 Showa Denko Kk Tube d'echangeur de chaleur et echangeur de chaleur
AU2003272090B2 (en) * 2002-10-02 2008-08-07 Showa Denko K.K. Heat exchanging tube and heat exchanger
US6973965B2 (en) * 2002-12-11 2005-12-13 Modine Manufacturing Company Heat-exchanger assembly with wedge-shaped tubes with balanced coolant flow

Cited By (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

Also Published As

Publication number Publication date
WO2006128684A1 (fr) 2006-12-07
RU2007149516A (ru) 2009-07-20
DE502006003328D1 (de) 2009-05-14
ATE427467T1 (de) 2009-04-15
AT501943A1 (de) 2006-12-15
EP1888992A1 (fr) 2008-02-20

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