The invention relates to a heat exchanger, in particular for motor vehicles, with a soldered heat exchanger network consisting of flat tubes and of corrugated ribs.
In the known heat exchangers for motor vehicles, such as coolant radiators, heating bodies, condensers and evaporators, the flat tubes have flowing through them a liquid and/or vaporous medium, for example a coolant or refrigerant, which discharges its heat to the ambient air or absorbs heat from the ambient air. To that extent, two very different heat capacity streams are in heat exchange with one another. In order to effect an equilibrium between the two sides, additional measures must to be taken on the air side in order to improve the heat transmission there. This is carried out by the arrangement of corrugated ribs between the flat tubes, as a result of which the heat exchange surface on the air side is enlarged. Furthermore, the surface of the corrugated ribs is slotted, that is to say equipped with gills, which break up the boundary layer flows that are formed and which bring about a deflection of the air flow from one flow duct into the other and consequently a prolongation of the flow path for the air.
Where the corrugated ribs are concerned, there are basically two different types, the V-type, as it is known, with rib surfaces arranged obliquely with respect to one another, known from U.S. Pat. No. 3,250,325. The second embodiment of the corrugated rib is what is known as the U-type, in which the rib surfaces and therefore also the gills arranged on them are oriented parallel to one another, this U-type having become known from U.S. Pat. No. 5,271,458. In thermodynamic terms, the U-type has some advantages as compared with the V-type, to be precise a relatively uniform throughflow of the approximately rectangular rib duct, a uniform flow deflection by the gills, a higher air throughput and consequently a higher heat transmission power. In manufacturing terms, the V-type is more advantageous, because various rib densities can be produced by gathering together or drawing apart the corrugated strip, while having a constant rib bending radius for the corrugation crest. By contrast, in the U-type, that is to say the parallel rib, as it is known, the rib density or the rib spacing is also fixed by the bending radius of the corrugation crest. The known parallel rib also has the disadvantage that the gill length is dependent on the rib bending radius, that is to say, the greater the radius, the shorter the gill is, this having a power-reducing effect.
It was therefore proposed to replace the rib bending radius by a flat piece which runs parallel to the tube wall and is soldered to the latter. The production of such a rectangular or meander-shaped corrugated rib is relatively complicated, corresponding production methods having been proposed in EP-B 0 641 615 and in EP-A 1 103 316. Although this “rectangular rib” has the advantage that the gills extend over almost the entire rib height (spacing from tube to tube), this is nevertheless at the expense of a high outlay in manufacturing terms.
The object of the present invention is to improve a heat exchanger of the type initially mentioned, in particular with a parallel rib, to the effect that the parallel rib has the advantages of a rectangular shape which, where appropriate, allows large gill lengths, that can however be produced at a relatively low outlay in manufacturing terms.
According to the invention, the known corrugation crest formed by a constant curvature is replaced by an arcuate piece which is composed of three portions having different curvatures. The middle portion has a comparatively low curvature, that is to say it has an almost planar design and therefore bears as much as possible against the outer surface of the tube wall. The radius of curvature of the arcuate piece is preferably greater in the middle region than a rib height RH of the corrugated rib, especially preferably 5 to 15 times the rib height RH.
This middle portion has adjoining it two outer portions having relatively high curvatures, but in this case the two curvatures may be different, so that the entire arcuate piece has an asymmetric profile with respect to the midplane. Preferably, a first outer portion has a radius of curvature R2 which is lower than half a rib height RH of the corrugated rib, especially preferably 3 to 20% of the rib height RH. A radius of curvature R3 of the second outer portion of the arcuate piece is preferably at least as high as the radius of curvature R2 of the first portion.
This rib geometry, in particular that of the arcuate piece, can be produced relatively simply on conventional rib rollers. Furthermore, the advantages of a parallel or rectangular rib are preserved, that is to say a relatively wide soldering surface with good heat transmission and, where appropriate, a large gill length which extends over almost the entire rib height. If the rib surfaces deviate somewhat (up to about 6 degrees) from parallelism, in which case they must still be considered as essentially parallel within the scope of the invention, the thermodynamic advantages of the parallel rib are scarcely impaired thereby. The rib geometry according to the invention can be used, in particular, in motor vehicle heat exchangers, such as coolant radiators, heating bodies, condensers and evaporators.
According to an advantageous element of the invention, the rib surfaces are equipped with gills which preferably have a gill depth LP in a range of 0.5 to 1.5 mm, especially advantageously in the range of 0.7 to 1.1 mm, with a gill angle of between 20 and 35 degrees, especially advantageously between 24 and 30 degrees. Such gills have a power-increasing effect, because the deflection of the air from one duct into the adjacent duct is thereby improved, thus resulting, in turn, in a longer flow path for the air.
Further advantageous refinements of the invention yield further power increases, particularly in the case of a tube/rib system with a depth of 12 to 20 mm and with a rib density of 55 to 75 ribs/dm, this corresponding to a rib spacing or a rib division of 1.33 to 1.82 mm. The rib height for this system is in the range of 3 to 15 mm, especially preferably in the range of 6 to 10 mm.
According to an alternative advantageous development of the invention, the gill depth in the range of 0.9 to 1.1 mm with a gill angle of 23 to 30 degrees is beneficial for a tube/rib system with a depth of 40 to 52 mm and with a rib density of 45 to 65 ribs/dm, this corresponding to a rib spacing of 1.538 to 2.222 mm. The rib height for such a system is advantageously 7 to 9 mm.
Exemplary embodiments of the invention are illustrated in the drawing and are described in more detail below. In the drawing:
According to the invention, two preferred exemplary embodiments having the following dimensions are optimal for the parallel rib described above:
The first exemplary embodiment relates to a condenser for an air conditioning system of a motor vehicle. Thus, refrigerant, for example R134a, flows through the flat tubes of the condenser. A heat exchanger network consisting of flat tubes and of a parallel rib having the following dimensions is provided for such a condenser:
A parallel rib system having the abovementioned dimensions is superior to a conventional rib system with a rib arranged in a V-shaped manner in many respects, specifically with regard to the air throughput, the flow deflection, the homogenization of the flow velocity and temperature profile and therefore the heat transmission power.
The second exemplary embodiment relates to a coolant refrigerator which is installed in motor vehicles in the coolant circuit for cooling the internal combustion engine and through which coolant, that is to say a water/glysantine mixture, flows. Parallel ribs having the following dimensions are provided between the flat tubes preferably arranged in a row:
This system, too, which is substantially deeper than the first exemplary embodiment, affords a marked increase in power in relation to a comparable V-rib.
Number | Date | Country | Kind |
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102 35 038 | Jul 2002 | DE | national |
Filing Document | Filing Date | Country | Kind | 371c Date |
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PCT/EP03/08251 | 7/25/2003 | WO | 00 | 4/22/2005 |
Publishing Document | Publishing Date | Country | Kind |
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WO2004/013559 | 2/12/2004 | WO | A |
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