EP2242979B1 - Tube filé pour échangeur de chaleur - Google Patents

Tube filé pour échangeur de chaleur Download PDF

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Publication number
EP2242979B1
EP2242979B1 EP08869782.6A EP08869782A EP2242979B1 EP 2242979 B1 EP2242979 B1 EP 2242979B1 EP 08869782 A EP08869782 A EP 08869782A EP 2242979 B1 EP2242979 B1 EP 2242979B1
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EP
European Patent Office
Prior art keywords
extruded tube
webs
web
extruded
transverse direction
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.)
Not-in-force
Application number
EP08869782.6A
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German (de)
English (en)
Other versions
EP2242979A1 (fr
Inventor
Jens Ruckwied
Ulrich Maucher
Peter Geskes
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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Publication of EP2242979A1 publication Critical patent/EP2242979A1/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
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded

Definitions

  • the invention relates to an extruded tube for a heat exchanger according to the preamble of claim 1 and a heat exchanger with an extruded tube according to the invention and to a method for producing an extruded tube according to the invention.
  • US 3,596,495 A describes by extrusion and drawing manufacturable tubes for a heat exchanger, in which according to an embodiment, a plurality of chambers are separated by inner webs.
  • the chambers are deformed by externally introduced dents both in the region of the side walls and in the region of the webs to produce turbulence of a fluid flowing through.
  • At least one of the channels of the extrusion tube in the longitudinal direction has a regular, wavy course with respect to the transverse direction.
  • the elongated imprint has an orientation angle to the transverse direction so that bulges of sidewalls and webs resulting from the same imprint are not at the same height in the longitudinal direction of the tube.
  • Such an orientation angle is approximately between 0 ° and 45 °, preferably approximately between 20 ° and 45 °, and particularly preferably approximately between 28 ° and 42 °.
  • At least one of the indentations is essentially only in overlap with the at least one web.
  • Another imprint can not be in overlap with a bridge.
  • indentations for bulging the side walls and embossments for buckling the webs are spatially separated from each other separately placed, so that there is a particularly large design opportunity for the formation of the channels.
  • Such an isolated embossment of a side wall may in particular have an orientation with respect to the transverse direction.
  • An orientation angle of this impression relative to the transverse direction may advantageously be approximately between 0 ° and 45 °, preferably approximately between 25 ° and 45 °, and particularly preferably approximately between 30 ° and 40 °.
  • At least one of the indentations may be winglet-shaped.
  • the winglet-shaped embossment has a ratio of length to width of between 2 and 5, preferably between 2.3 and 4 and particularly preferably between 2.5 and 3.2.
  • the winglet-shaped embossing has a ratio of length to width of between 1.2 and 5, preferably between 1.5 and 3 and particularly preferably between 1.8 and 2.5.
  • the orientations of at least some bulges of adjacent webs, which lie substantially at the same height in the longitudinal direction are the same. This allows a substantially constant cross-section of the channel at least with respect to the transverse direction, so that the risk of blockages due to deposits, for example, when used for exhaust gas cooling, is low.
  • a buckling of one of the side walls and a bulging of the web are provided alternately one behind the other in the longitudinal direction of a channel in order to produce a uniform turbulence in all spatial directions.
  • a bulging of the web in a first orientation in the transverse direction, followed by a bulging of a first of the two side walls, following a bulging of the web in the respective other orientation and subsequent bulging of the respective other side wall is particularly advantageous.
  • a screwed course of the channel is generated, which advantageously acts on the fluid flow with a swirl.
  • a plurality of such sections may be provided with in particular different swirl direction.
  • a further advantageous embodiment provides to make the bulging of the webs and / or the channel walls alternately in opposite directions, so that there is an alternating acceleration and deceleration of the flow.
  • bulges of two webs delimiting the channel at the same height lie opposite each other and are directed toward one another, so that the channel width is reduced by the bulges.
  • an acceleration of the flow can be achieved at this bottleneck.
  • bulges in the longitudinal direction of a channel two of the channel limiting webs lying at the same height, facing away from each other have bulges, so that the channel width is increased by the bulges.
  • a slowdown of the flow can be achieved at this point.
  • alternate broadening and narrowing of the channels may also be provided.
  • the bulge of the web is formed both by an impression of the first side and an at least partially overlapping impression of the second side.
  • a particularly clear bulging of the web can be achieved with only a slight bulging of the side walls.
  • the orientation of the bulge with respect to the embossed imprints is opposite.
  • the orientation of the bulge is rectified with respect to the embossed impressions.
  • the controlled-oriented bulging of the web takes place by means of a stamping tool inclined relative to the side walls.
  • a transversely oriented force is exerted on the web, so that the direction of its bulging or buckling is predetermined.
  • the controlled-oriented bulging of the web takes place by means of an embossing tool acting off-center relative to the web.
  • the embossing tool can be only about as wide as the web in the transverse direction and the deviation of the embossing center of the web center be relatively low, so that a controlled directed buckling of the web and on the other hand, the side wall adjacent to the web as little as possible in the High direction is dented.
  • an end-side region of the extrusion tube is preferably not provided with bulges.
  • One Distance of a pipe end to a first embossing is advantageously about between 2 mm and 15 mm, more preferably between about 4 mm and 8 mm.
  • a distance of a pipe end up to a first embossing is advantageously between approximately 4 mm and 20 mm, particularly preferably approximately between 6 mm and 12 mm.
  • an extruded tube has a bent region, so that the heat exchanger may be, for example, a U-flow heat exchanger or is generally adapted by the bending of the tubes to a predetermined space.
  • the heat exchanger may be, for example, a U-flow heat exchanger or is generally adapted by the bending of the tubes to a predetermined space.
  • the heat exchanger may be, for example, a U-flow heat exchanger or is generally adapted by the bending of the tubes to a predetermined space.
  • the heat exchanger may be, for example, a U-flow heat exchanger or is generally adapted by the bending of the tubes to a predetermined space.
  • the tube material consists of one of the group aluminum alloy, AlMn alloy, AlMg alloy and AlMgSi alloy.
  • Such light metal alloys are particularly easy to extrude and deformable with the indentations according to the invention. It has been found that extruded tubes made of such alloys, even when used as an exhaust gas cooler, have good corrosion resistance to aggressive condensate.
  • a depth of the impressions is less than about 75%, preferably less than about 45%, and more preferably less than about 30% of an inner tube diameter in the vertical direction.
  • a distance between an embossing of the underside of the tube to a subsequent embossing of the tube top side is advantageously not more than 10 times, preferably not more than 6 times and particularly preferably not more than 3, 5 times an inner pipe diameter in the vertical direction is.
  • an optimized execution has the property that in the In the longitudinal direction, a distance between an embossment for bulging a side wall to a subsequent embossment for bulging a web is not more than 8 times, preferably not more than 6 times and particularly preferably not more than 3 times an inner pipe diameter in the vertical direction is.
  • a length of the embossing in the transverse direction is optimally approximately between 25% and 100%, preferably between 35% and 90% and particularly preferably between 45% and 80% of a width of the extruded tube in the transverse direction.
  • their length in the transverse direction is approximately between 25% and 130%, preferably between 35% and 95% and particularly preferably between 45% and 75% of a width of the channel bounded by the webs transverse direction.
  • a rib member is arranged, in particular by means of material connection. This may in particular be a surface soldering.
  • material connection This may in particular be a surface soldering.
  • a repeat unit of the indentations in the longitudinal direction and a repeat unit of ribs of the rib member are not integer multiples of each other. As a result, unfavorable regular overlaps of contact surfaces of the ribs can be avoided with embossed areas of the tube surface.
  • At least one half-leg may project from one of the side walls into one of the channels.
  • one is four times the ratio of the area of the flow-through cross-section to a through the first fluid wettable perimeter of defined hydraulic diameters in a range between 1.2 mm and 6 mm.
  • preferred ranges of the hydraulic diameter are between about 2 mm and about 5 mm, particularly preferably between 3.0 mm and 3.4 mm, particularly preferably between 3.1 mm and 3.3 mm and in particular about 3.2 mm.
  • the hydraulic diameter (ie) is advantageously between about 2.5 mm and 4 mm, particularly preferably between about 2.8 mm and 3.8 mm.
  • the hydraulic diameter (ie) is advantageously in a range between 2 mm and 3.5 mm, particularly preferably between 2.5 mm and 3.5 mm.
  • a ratio of the hydraulic diameter (dh) and a channel shell thickness (s) is advantageously in a range between 0.8 and 8, preferably in a range between 1.2 and 6 and particularly preferably in a range between 1,4 and 6.
  • a ratio of a web thickness (d) and a channel shell thickness (s) is preferably below 1.0.
  • a ratio of a circumference of the extruded tube and the circumference wetted by the first fluid lies in a range between 0.1 and 0.9, in particular between 0.1 and 0.5, the latter range being particularly suitable for exhaust gas coolers.
  • a ratio of a distance (e) between two in particular opposite and / or staggered partial webs to a height (b) of the pipe cross-section is in a range below 0.8, more preferably in a range between 0.3 and 0.7 is.
  • a ratio of a distance (a3) a first partial web to a full web to a distance (a4) of a second partial web to the whole web is preferably in a range between 0.5 and 1.0, particularly preferably in a range between 0.6 and 0.8 in a corresponding design.
  • At least one web and / or the channel jacket, preferably the channel jacket inner side has a corrosion protection, preferably in the form of a galvanizing and / or a paint.
  • a cross section of the extruded tube may advantageously be rectangular, oval or semi-oval, for example.
  • a number of 2 to 20, preferably 5 to 15, more preferably 7 to 12, particularly preferably 8 to 11 and particularly preferably 9 webs are arranged side by side over a tube cross-section.
  • the object of the invention is also achieved according to claim 11 by a heat exchanger with an extruded tube according to the invention.
  • a first fluid is passed, which exchanges heat with a second fluid flowing around the tube outside.
  • Such heat exchangers find widespread use, especially in motor vehicles, whereby optimization of the heat exchange performance due to the indentations according to the invention is particularly advantageous due to the high demands on weight and installation space.
  • the extruded tubes are circulated air.
  • the extrusion tubes can also be flowed around by a cooling liquid, for example in the case of an indirect exhaust gas cooler of a motor vehicle.
  • the heat exchanger according to the invention may be an exhaust gas cooler for cooling a recirculated exhaust gas flow, but also a charge air cooler of an internal combustion engine, an oil cooler or a coolant radiator. Particularly preferably, these heat exchangers are each used in a motor vehicle.
  • the object of the invention is achieved by a manufacturing method for the extrusion tube by the features of claim 17.
  • the extruded profiles are first formed in the manner of a continuous prismatic body by a known extrusion process and subsequently introduced the imprints. This can take place in a step immediately following the extrusion, in particular also when the profile is still warm, or else in a completely separated step on a cooled and / or interposed profile strand.
  • the embossing is effected by means of an embossing roller. Alternatively or additionally, however, it can also be done by means of an embossing stamp.
  • a stamping subsequent step of separating the extruded tubes is provided by an endless or quasi-endless profile strand to optimize the manufacturing cost. This can be done for example by a sawing process. In a particularly advantageous detailed design, however, the separation takes place by a tearing off, in particular after a previous scoring. As a result, the occurrence of chips in the course of the separation can be largely avoided.
  • the orientations of at least some bulges of adjacent webs which lie in the longitudinal direction substantially at the same height, opposite, being preferred in the longitudinal direction of a channel a bulge of one of the side walls and a bulge of the web are provided alternately one behind the other, wherein preferably in the longitudinal direction of a channel initially a bulge of the web in a first orientation in the transverse direction, followed by a bulge of a first of the two side walls, below a bulging of the web in the respective other orientation and subsequent bulging of the respective other side wall, wherein preferably in the longitudinal direction of a channel bulges of the channel delimiting two webs lying at the same height, oppositely directed bulges have, so that the channel width is reduced by the bulges , wherein preferably in the longitudinal direction of a channel bulges of the channel delimiting two webs lying at the same height, directed away from each other buckling, so that the channel width is increased by the bulges, wherein preferably the Ausb e
  • the controlled-oriented bulging of the web is effected by means of an embossing tool inclined relative to the side walls, wherein preferably the controlled-oriented bulging of the web takes place by means of an embossing tool engaging eccentrically relative to the web, preferably an end-side region of the extruded tube not provided with bulges is, wherein preferably a distance of a pipe end to a first embossing is approximately between 2 mm and 15 mm, in particular approximately between 4 mm and 8 mm.
  • the extruded tube has a bent region, wherein preferably in the bent region an at least reduced depth of the bulges, preferably in the bent portion at least partially no bulges are arranged, wherein preferably the tube material from one of the group aluminum alloy, AlMn Alloy, AlMg alloy and AlMgSi alloy
  • a depth of the impressions is less than about 75%, in particular less than about 45%, in particular less than about 30% of an inner tube diameter in the vertical direction, preferably in the longitudinal direction
  • a distance between an impression of a side wall to a subsequent impression of the other side wall is not more than 10 times, in particular not more than 6 times, in particular not more than 3.5 times an inner tube diameter in the vertical direction
  • a distance between an impression for buckling a side wall to a subsequent embossment for buckling a web is not more than 8 times, in particular not more than 6 times, in particular not more than 3 times an inner
  • a rib element is arranged on at least one of the side walls from the outside, in particular by means of a material-locking connection, preferably a repeat unit of the indentations in the longitudinal direction and a repeat unit of ribs of the rib element are not integer multiples of each other, wherein preferably at least one half-leg of a the side walls protrudes into one of the channels.
  • a hydraulic diameter defined as four times the ratio of the area of the flow-through cross-section to a periphery wettable by the first fluid is in a range between 1.2 mm and 6 mm, wherein the hydraulic diameter is preferably between approximately 2 mm and about 5 mm, in particular between 3.0 mm and 3.4 mm, in particular between 3.1 mm and 3.3 mm, in particular about 3.2 mm, wherein preferably the hydraulic diameter between about 2.5 mm and 4 mm, in particular between about 2.8 mm and 3.8 mm, in particular for a high pressure heat exchanger, preferably the hydraulic diameter is in a range between 2 mm and 3.5 mm, in particular between 2.5 mm and 3.5 mm, in particular for a low-pressure heat exchanger, preferably a ratio of the hydraulic diameter and a channel sheath thickness in a range between 0.8 and 9, in particular in a range between 1.2 and 6, in particular in a range between 1.4 and 6, wherein preferably a ratio of a web
  • the extruded tubes of the heat exchanger are circulated air, wherein preferably the extruded tubes are flowed around by a cooling liquid, wherein preferably the heat exchanger Exhaust gas cooler for cooling a recirculated exhaust gas flow, a charge air cooler, an oil cooler or a coolant radiator is.
  • the embossing is effected by means of an embossing roll, wherein preferably the embossing is effected by means of a stamping die, wherein preferably the embossing is followed by a step of separating the extruded tubes from an endless or quasi-endless profile strand, wherein preferably the separation by a sawing process or by a tear-off, in particular after a previous scoring takes place.
  • the invention relates to extruded tubes which extend at least in sections in a longitudinal direction designated z.
  • the extruded tubes have an elongated extension transversely to the longitudinal direction, wherein they are in particular formed as flat tubes.
  • a transverse direction in the sense of claim 1 is in Fig. 1 referred to as y-direction, wherein the (long) side walls 1, 2 of the extruded tube extend substantially in this direction.
  • a high direction is in Fig. 1 denoted by x and extends perpendicular to the longitudinal direction and the transverse direction.
  • the side walls 1, 2 do not necessarily have to extend straight in cross-section but can also run in a curved manner and in this sense are oriented only "substantially" in the transverse direction or "at least approximately parallel".
  • the side walls 1, 2 are connected to each other via shorter, curved, substantially in the vertical direction extending narrow sides 3, 4 to form a closed flat tube.
  • the side walls are connected via a plurality of continuous webs 5, 79, 89 with separation of separate channels 6.
  • continuous webs or full webs 5, 79, 89 may optionally (see, for example Fig. 4 or FIGS. 10A to 11B ) also partial webs 5 ', 79', 89 'are provided, which protrude in the manner of fins to increase the contact area between the channel wall and fluid in the channels 6.
  • indentations 7 are formed by the longitudinal direction with respect to local bulges, which protrude into the channels 6 and influence the fluid flow.
  • These may be bulges of the side walls 1, 2, which protrude correspondingly in the vertical direction or even buckling or buckling of the continuous webs 5, 79, 89, which protrude accordingly in the transverse direction.
  • Such bulges of the webs are achieved in that an impression is made at least partially covering the neck region of the web on the side wall.
  • a check of the buckling direction can also be achieved for punctiform impressions.
  • the example C is the Fig. 3 a serrated embossing edge 8b shown only with small local projections or punctiform attacks on the extrusion tube.
  • the points of attack are essentially located over the webs 5, but slightly eccentric to it.
  • This also buckling of the webs 5 is achieved in a predetermined orientation with respect to the transverse direction.
  • the direction of the bulging of the webs 5 would also be in the example C to the right, since the embossing points each attack slightly to the left of the center of the webs 5.
  • embossing stamps 8 alternative or complementary possibility of a substantially point-like embossment with local projections over the in Fig. 7 shown embossing roll 9 with point-like local projections 10 given.
  • embossing roller 9 ' shown has elongate projections 10', which extend over at least an entire channel width or over the substantially entire width of the extruded profile.
  • embodiments such as those in Fig. 4 be prepared, with the local projections of the embossing roll 9 versions as in Fig. 6 and Fig. 6a can be produced.
  • the two types of projections 10, 10 ' can also be provided together on the same embossing roller.
  • a first embodiment is essentially according to Fig. 2 and a second extrusion tube Fig. 6 each shown with several modifications.
  • the first embodiment Fig. 2 it is impressions of the first type with smooth, inclined embossing edges, each overlap more than one web 5 of the extruded tube at the same time and thus at the same time bulge the side walls between the webs inwards.
  • the embossing edges or indentations are arranged at an orientation angle relative to the transverse direction.
  • the impressions are expediently made in both side surfaces 1, 2. These opposite impressions can overlap (eg Fig. 2 Ex. 2.2, 2.4) or alternatively arranged offset in an alternating manner (eg 2.1, 2.3).
  • the orientation angles of the impressions can vary and, in particular, alternate as in Examples 2.5, 2.8 and 2.9. It can be provided over the width of the extruded tube also several transversely shorter embossments with varying orientation angles, see for example Examples 3.6 to 3.9.
  • the bulging directions of the webs are made by impressions from above opposite those in the longitudinal direction alternately from below impressions to achieve the highest possible turbulence generation at moderate pressure loss increase.
  • the indentations in the longitudinal direction are alternately mounted in the form that in the flow longitudinal direction after an expression of the pipe webs an expression of the pipe wall takes place and then again an expression of the pipe webs etc.
  • the manifestations may additionally be applied alternately on both side walls 1, 2 and in particular in the form that in the longitudinal direction after buckling of a web 5 in one direction by an indentation 7 on the upper side wall 1 an impression of the lower side wall 2 takes place, in the longitudinal direction below the buckling of a web 5 in the other orientation direction by an impression 7 on the lower side wall 2 and longitudinally following an impression 7 of the upper side wall 1.
  • Fig. 6 shows advantageous impressions example of a pipe with three intermediate webs 5.
  • the impression of the upper side wall 1 in dashed line the impression of the lower side wall 2 is shown.
  • An arrow shows the direction of the ridge buckling.
  • the indentations in the x-, y-, and z-directions can be round, oval, oval oblong rectangular or even in another form.
  • the impressions are made alternately as described above.
  • the deformation of the sewer pipe wall at one point can be carried out by one or even two characteristics per channel (see, for example, Examples 6.4, 6.5, 6.9 and 6.10). However, in special cases, especially with very wide channels, this can also be done by more than two impressions in one place.
  • Fig. 6.3 are impressions of the side walls 1, 2 shown between the webs 5, which are aligned at a defined orientation angle to the transverse direction.
  • the orientation angle of the indentation with respect to one of the axes z and y in the present case is approximately between 30 ° and 40 °.
  • the examples 6.4, 6.5, 6.9 and 6.10 show variants with winglet-like, ie oblong and preferably angled embossed impressions between the webs 5.
  • any combination of winglets to each other both in position and orientation to each other as well Direction of the bars conceivable.
  • an orientation angle of the embossment with respect to one of the axes z and y is particularly preferably between about 28 ° and 42 °.
  • the shape of the winglets is chosen so that the ratio of their length to their width is a multiple, in particular about 1.8 times to 2.5 times or about 2.5 times to 3.2 times.
  • impressions between the webs 5 in winglet shape over simpler embossed impressions have the advantage that with this type of flow control even higher heat transfer performance can be achieved because the flow undergoes an even more directed deflection with a much higher turbulence.
  • the bulges of the webs 5 are designed so that they always bulge in the transverse direction in the same orientation, so that the free channel spacing between adjacent webs 5 does not or only slightly changes. In the longitudinal direction, the webs thus have a parallel waveform with respect to each other with respect to the transverse direction.
  • Examples 6.14 and 6.15 illustrate another possibility of having both the side wall and the web / the limiting webs buckling with only one indentation in that the stamp, in addition to the channel width, also has a part or more of that of the adjacent one Footbridges covered.
  • Variants shown are all conceivable combinations of ridge buckling for Kanalein rempligungscardi conceivable here.
  • the required distance of the profile end to the first embossing is particularly dependent on the depth of the impressions.
  • the distance is to be selected so that in the area of the joint no or only a very small deformation of the original pipe geometry occurs. In typical cases of heat exchangers dimensioned for use in motor vehicles, this means a distance between 2-15mm, especially 4-8mm. In special cases, however, this measure can also go beyond these distances.
  • indentations are dispensed with in the region of the bend in order to prevent excessive deformation and possibly even closure of individual channels.
  • the embossing depth can only be reduced or, for example, only one embossing of the webs or only a constriction of the channel walls can be provided. In the manufacturing process, first the embossing of the tubes and then the bending into the desired shape.
  • the embossment can be produced both in one stage and in several stages via a plurality of embossing rollers or sets of punches provided one after the other in the direction of production.
  • the extrusion tube is held by means of at least one holding function before and / or after the embossing stage in position.
  • a lateral roller guide ensures that the extrusion tube does not shift in the transverse direction during the stamping process. If the deflection of the extruded tube can only be partially prevented by means of this holding function, this can be corrected by means of a subsequent working step by stretching or recalibrating the extruded tube via a further set of rollers or a press.
  • embossing by means of rolling has the advantage that the process can be carried out with continuous feed of the extruded tube, while for the production by means of stamp sets usually a clocking of the feed is necessary.
  • the latter can be provided for the embossing by means of rollers, for example by a corresponding geometry of the embossing roller.
  • the roll circumference always corresponds to an integer multiple of the later profile length.
  • Another way to provide a sufficiently wide sawing or joining area is to perform the delivery of the rollers variable, so that depending on the delivery of the rolls either imprints are formed or not.
  • a further advantage of production by means of rollers is that different profile variants can be produced by exchanging the rollers in a very simple way with the same production line.
  • embossing rolls In addition to an exchange of the embossing rolls, it is alternatively also possible to work with only one embossing roll into which the embossing embossments are introduced in such a way that they are interchangeable. In this case, work is done with a base roll in which variable embossing sets can be used. Alternatively, it is also conceivable to draw on a base roll without or with a few forms an additional filler, which occupies the desired embossing arrangement. In both cases, working with only one roller body.
  • the stamps in the sawing and joining area must be completely or partially exposed to obtain a large sawing area, so that no or only very weak embossments are produced.
  • the separation is preferably carried out by means of a saw running along with the embossing process, but can also take place in a separate sawing process following the embossing process.
  • the separation of the extruded tubes can also be done by scoring and then tearing off the tubes. This has the advantage that no chips arise and no additional sheschmmierstoff is needed. As a result, depending on the application, it may be possible to completely or partially dispense with a subsequent cleaning step.
  • the stamped extruded tubes can be produced with any extrudable material.
  • heat exchangers such as exhaust gas coolers, oil coolers, coolant coolers and intercoolers, are all extrudable aluminum alloys, in particular Al alloys, in particular AlMn alloys, AlMg alloys and AlMgSi alloys.
  • a particularly high corrosion resistance of these extruded tubes can generally be achieved if the particle sizes measured in the extrusion direction are ⁇ 250 ⁇ m, in particular ⁇ 100 ⁇ m, in particular ⁇ 50 ⁇ m.
  • the depth of the impression depends very much on the application. However, it has been shown that, particularly from the viewpoint of material thinning and the pressure loss generated by the indentation, an indentation depth of less than 75% of the clear tube height b, in particular less than 45%, in particular less than 30%, has proven to be advantageous.
  • An extrusion tube according to the concept of the invention can be used advantageously both in the context of high-pressure exhaust gas recirculation and in the context of low-pressure exhaust gas recirculation. Furthermore, an application for a charge air cooling or coolant cooling is possible. In all, in particular those mentioned or similar, applications, an increase in the number of webs to improve the heat transfer according to the concept of the invention is avoided by the hydraulic diameter is selected in a range between 1.2 mm and 6 mm. However, tests have shown that a choice of a range for the hydraulic diameter optimized with regard to a low-pressure exhaust gas recirculation, high-pressure exhaust gas recirculation or intercooling can be designed differently.
  • a channel casing thickness such that corrosion resistance on the one hand, in particular in the case of an extruded tube based on an aluminum material, is ensured to a sufficient extent and, on the other hand, to provide a sufficient number of extruded tubes in the available installation space of a heat exchanger.
  • a space for a heat exchanger in a motor is comparatively limited, so that it is fundamentally within the scope of an improvement to provide as many extruded tubes in a heat exchanger available and thus not to design a Kanalmantelstar too thick.
  • a ratio of the hydraulic diameter and a channel shell thickness in a range between 0.8 and 9 has proven to be particularly advantageous.
  • This area has proved to be particularly useful, especially in an extruded tube based on an aluminum material, in particular in an extruded tube in which at least the channel jacket is based on an aluminum material. Also advantageous is a range between 1.2 and 6.0, in particular a range between 1.4 and 6 with regard to the design of the channel casing thickness (space requirement, corrosion resistance) and the hydraulic diameter (heat transfer, pressure loss).
  • an extruded tube proves in the pipe cross section a web is arranged as a whole web at one end and the other end on the channel jacket inside.
  • a pipe cross-section may only have full webs.
  • a whole web is continuous, without openings, executed between a first channel jacket inner side and a second channel jacket inner side.
  • an extruded tube has proved to be advantageous in which a web is arranged as a partial web in the tube cross-section only one end of the channel inside and the other freely protrudes into the interior.
  • 10A and 10B such as FIGS. 11A and 11B explained, can be realized on the basis of an extruded flow channel in a particularly advantageous manner, a hydraulic diameter according to the concept of the invention.
  • two partial webs can be arranged with end faces lying opposite one another.
  • two partial webs may be arranged with mutually laterally offset end faces.
  • a partial web and a whole web are alternately arranged next to one another.
  • a ratio of a distance between two part-standing, in particular two opposite partial webs and / or two mutually offset partial webs, to a height of the pipe cross section in a range below 0.8, preferably in a range of 0.3 and 0.7.
  • a ratio of a distance of a first partial web to a full web to a distance of a second partial web to the full web in a range between 0.5 and 1.0, preferably in a range between 0.6 and 0.8.
  • Fig. 8 represents the ratio of the volume wetted by a fluid, such as exhaust gas, and an outer circumference of the extruding tube as a function of the hydraulic diameter.
  • a preferred ratio results from the hatched areas of a preferred hydraulic diameter of 2 mm to 5 mm, in particular 2, explained above , 8 mm to 3.8 mm.
  • Out Fig. 8 It can be seen that said ratio should be in the range between 0.1 and 0.5 in order to achieve improved degrees of exchange and pressure loss.
  • Fig. 8 is an example of an in 10B specified profile of an extrusion tube at-exemplified. A comparable tendency can be observed even in the case of the further constructive embodiments of a flow-through cross-section described below in more detail in the case of an extruded tube.
  • the ratio k should be as in Fig. 8 represented by arrows, in a range below 0.8, preferably in a range between 0.3 and 0.7.
  • the ratio k of a distance e between two opposing partial webs to a height b of the pipe cross-section increases from 0.25 to 0.75 in the direction of the arrow.
  • This analysis applies both to an exhaust gas cooler in the context of a high-pressure design in an exhaust gas recirculation system and to an exhaust gas cooler in the context of a low-pressure design in an exhaust gas recirculation system.
  • FIGS. 9A to 11B exemplary constructive embodiments of a cross section of different preferred extrusion tubes described. It should nevertheless be clear that modifications thereof as well as any combination of features of the concretely described in the figures embodiments are possible and yet a hydraulic diameter in the range between 1.5 mm and 6 mm, preferably between 2 mm and 5 mm, preferably between 2.8 mm and 3.8 mm can be achieved.
  • a modification is shown, in which a channel shell thickness and a web thickness d are the same and a further modification is shown in which a ratio of a web thickness d and a channel shell thickness s below 1, 0 mm. Accordingly, the wall thicknesses of partial webs or similar dimensions, depending on the purpose to be achieved, vary and adapt.
  • Figs. 9A and 9B show two modifications of an extrusion tube 61, 61 ', wherein the modifications differ in that the shell thickness s in the in Fig. 9B shown extrusion tube 61 'is thicker than a web thickness d, while this in the in Fig. 9A shown extrusion tube 61 are substantially equal.
  • the same reference numerals are used for the same features.
  • the flow channel 61, 61 ' is formed as a total extruded profile, ie as an extruded channel casing together with the extruded webs.
  • the flow channel 61, 61 ' accordingly has a channel jacket 63 with an interior 67 surrounded by a channel jacket inner side 65, which in the present case is designed to heat-exchange the first fluid in the form of an exhaust gas.
  • the flow channel 61, 61 'in the present case has a number of five webs 69 arranged in the inner space 67 on the channel casing inner side 65, which webs are formed together with the channel casing 63, 63' as an integral extruded profile.
  • a web 69 extends completely parallel to a flow channel axis perpendicular to the plane of the drawing, along the flow path formed in the housing of a heat exchanger, uninterruptedly.
  • the design is based on the hydraulic diameter ie, for the present extrusion tube 61, 61 'with reference to the distances a, b in the lower right in Fig. 9B is specified.
  • the hydraulic diameter is given as four times the ratio of the area of the flow-through cross-section to a wettable by the exhaust gas perimeter.
  • the area of the flow-through cross section is presently a multiple of the product of a and b.
  • the wettable circumference here is also the multiple of twice the sum of a and b.
  • a indicates the width of the free cross section of a flow line 74 subdivided by the webs 69 in the flow channel, and b indicates the free height of the streamline 74 in the present case.
  • a wall thickness s in the range between 0.2 mm and 2 mm, for corrosion-critical applications preferably in the range between 0.5 mm and 1.4 mm, for corrosion-critical applications preferably in the range between 0.3 mm and 0.8 mm.
  • a height b of a flow thread 74 or a height of the inner space 67 in the present case is in the range between 2.5 mm and 10 mm, preferably in the range between 4.5 mm and 7.5 mm.
  • a width a of a channel 74 in the transverse direction is in the range between 3 mm and 10 mm, preferably in the range between 4 mm and 6 mm.
  • 10A.2 and 10B.2 show two further modifications of a particularly preferred embodiment of an extrusion tube 71, 71 ', which - as explained above - differ only in the wall thickness of the channel jacket 73, 73' relative to the wall thickness of a web 79.
  • the flow channel 71, 71 ' also has the webs 79 in the form of full webs and next to them alternately to the full webs 79 arranged partial webs 79'.
  • the extrusion tube 71, 71 ' is in turn formed entirely as an extruded profile, wherein a channel 74 is again formed by the distance between two full webs 79.
  • a ratio of a distance a3 of a first partial web 89 'to a full web 89 to a distance a4 of a second partial web 89' to the whole web 89 is in a range between 0.5 mm and 1.0 mm, preferably in a range between 0.6 mm and 0.8 mm.
  • the distance e between two opposite partial webs 79 'and / or between two mutually offset partial webs 89' to a height b of the tube cross-section in a range below 0.8 mm, in particular in a range between 0.3 mm and 0.7 mm.
  • FIGS. 9A to 11B shown preferred extruded tubes according to the invention with indentations and bulges according to the illustrated embodiments provided to optimize the turbulence and the heat transfer and the pressure drop in the concrete application.
  • FIGS. 12 and 13 show each other versions 91, 101 of cross sections of not bulged extruded tubes.
  • partial webs 92, 102 which extend transversely into the channels 6, starting from the webs 5.
  • the partial webs are each arranged at the same height and in the example according to Fig. 13 at different heights.
  • FIGS. 12 and 13 are true to scale, so that they can be taken from certain dimensions of the drawn dimensions.

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

Claims (12)

  1. Tube extrudé pour un échangeur de chaleur, comprenant deux parois latérales extérieures (1, 2), au moins presque parallèles, qui s'étendent dans une direction longitudinale (z) et dans une direction transversale (y) du tube extrudé et sont assemblées au moyen de deux petits côtés extérieurs (3, 4), suivant une direction (x) dans le sens de la hauteur du tube extrudé, où au moins deux nervures continues (5) s'étendent entre les parois latérales (1, 2) dans la direction longitudinale (z) et dans la direction (x) dans le sens de la hauteur et séparent au moins trois canaux (6) du tube extrudé, et où au moins l'une des parois latérales extérieures (1, 2) présente des parties matricées en creux (7) au moyen desquelles sont formées aussi bien des parties en saillie des parois latérales (1, 2), lesdites parties en saillie pénétrant dans les canaux (6), ainsi que des parties en saillie des nervures (5), lesdites parties en saillie s'étendant sensiblement suivant une direction transversale (y), caractérisé en ce que les parties formées en saillie de l'une des nervures (5) au moins au nombre de deux présentent une orientation contrôlée par rapport à la direction transversale (y), où au moins l'une des parties matricées en creux (7) présente une forme oblongue, où une pluralité de nervures (5) est recouverte et formée en saillie par la même partie matricée en creux (7), et la partie oblongue matricée en creux (7) présente un angle d'orientation par rapport à la direction transversale (y), où l'angle d'orientation est compris à peu près entre 0° et 45°, en particulier à peu près entre 20° et 45°, en particulier à peu près entre 28° et 42°.
  2. Tube extrudé selon la revendication 1, caractérisé en ce qu'au moins l'un des canaux (6) du tube extrudé présente, dans la direction longitudinale (x), un profil régulier et de forme ondulée par rapport à la direction transversale (y).
  3. Tube extrudé selon l'une ou l'autre des revendications précédentes, caractérisé en ce qu'un intervalle est sensiblement constant entre deux nervures voisines (5), dans la direction transversale (y).
  4. Tube extrudé selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins l'une des parties matricées en creux (7) coïncide pratiquement seulement avec la nervure (5) au moins au nombre de un.
  5. Tube extrudé selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins l'une des parties matricées en creux (7) ne coïncide pas avec une nervure (5).
  6. Tube extrudé selon la revendication 5, caractérisé en ce que la partie matricée en creux (7) présente une orientation par rapport à la direction transversale (y).
  7. Tube extrudé selon la revendication 6, caractérisé en ce qu'un angle d'orientation de la partie matricée en creux (7), par rapport à la direction transversale (y), est compris à peu près entre 0° et 45°, en particulier à peu près entre 25° et 45°, en particulier à peu près entre 30° et 40°.
  8. Tube extrudé selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins l'une des parties matricées en creux (7) est configurée en forme de winglet, comme étant oblongue.
  9. Tube extrudé selon la revendication 7, caractérisé en ce que la partie matricée en creux (7) en forme de winglet présente un rapport de la longueur relativement à la largeur compris entre 1,2 et 5, de préférence entre 2 et 5, de façon particulièrement préférable entre 2,5 et 3,2, ou bien de préférence entre 1,5 et 3, de façon particulièrement préférable entre 1,8 et 2,5.
  10. Tube extrudé selon l'une quelconque des revendications précédentes, caractérisé en ce que les orientations d'au moins quelques parties formées en saillie de nervures voisines (5) qui sont sensiblement à une même hauteur dans la direction longitudinale, sont identiques.
  11. Echangeur de chaleur pour un véhicule automobile, comprenant un tube extrudé selon l'une quelconque des revendications précédentes.
  12. Procédé de fabrication d'un tube extrudé selon l'une quelconque des revendications 1 à 11, comprenant les étapes
    - de fabrication du tube extrudé par un procédé d'extrusion et, ensuite,
    - de matriçage en creux des parties matricées en creux dans les parois latérales (1, 2).
EP08869782.6A 2008-01-10 2008-12-18 Tube filé pour échangeur de chaleur Not-in-force EP2242979B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008003737 2008-01-10
PCT/EP2008/010829 WO2009086894A1 (fr) 2008-01-10 2008-12-18 Tube filé pour échangeur de chaleur

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EP2242979A1 EP2242979A1 (fr) 2010-10-27
EP2242979B1 true EP2242979B1 (fr) 2014-09-24

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EP (1) EP2242979B1 (fr)
JP (1) JP2011509393A (fr)
KR (1) KR20100106434A (fr)
CN (1) CN101910774A (fr)
DE (1) DE102008062704A1 (fr)
WO (1) WO2009086894A1 (fr)

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JP2011509393A (ja) 2011-03-24
DE102008062704A1 (de) 2009-08-27
CN101910774A (zh) 2010-12-08
US20110000657A1 (en) 2011-01-06
KR20100106434A (ko) 2010-10-01
WO2009086894A1 (fr) 2009-07-16
EP2242979A1 (fr) 2010-10-27

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