EP2242979A1 - Tube filé pour échangeur de chaleur - Google Patents

Tube filé pour échangeur de chaleur

Info

Publication number
EP2242979A1
EP2242979A1 EP08869782A EP08869782A EP2242979A1 EP 2242979 A1 EP2242979 A1 EP 2242979A1 EP 08869782 A EP08869782 A EP 08869782A EP 08869782 A EP08869782 A EP 08869782A EP 2242979 A1 EP2242979 A1 EP 2242979A1
Authority
EP
European Patent Office
Prior art keywords
extruded tube
web
webs
extruded
tube according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08869782A
Other languages
German (de)
English (en)
Other versions
EP2242979B1 (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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP2242979A1 publication Critical patent/EP2242979A1/fr
Application granted granted Critical
Publication of EP2242979B1 publication Critical patent/EP2242979B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 a method for producing an extruded tube according to the invention.
  • US 3,596,495 A describes producible by extrusion and drawing 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.
  • turbulence and heat transfer are thereby increased and, on the other hand, bottlenecks are avoided which can cause excessive pressure drop and possibly blocking due to the addition of fluid or substances precipitated from the fluid.
  • a distance in the transverse direction between two adjacent webs substantially constant.
  • At least one of the indentations has an elongate shape, wherein a plurality of webs is covered and bulged by the same indentation.
  • the oblong embossment has an orientation angle to the transverse direction, so that bulges of sidewalls and webs resulting from the same embossment are not at the same height in the longitudinal direction of the tube.
  • Such an orientation angle is advantageously approximately between 0 ° and 45 °, preferably between approximately 20 ° and 45 °, and particularly preferably approximately between 28 ° and 42 °.
  • the oblong indentation has an alignment parallel to the webs and / or is arranged offset over the webs or only slightly offset from the webs.
  • the embossing has a length which is 1, 1 to 3.25 times, in particular 1.35 to 2.45 times, in particular 1.62 to 2.16 times the channel width.
  • 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 indentation with respect to the transverse direction can 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.
  • a largely constant cross-section of the channel is made possible, at least with regard to the transverse direction, so that the risk of blockages due to deposits conditions, for example when used for exhaust gas cooling, is low.
  • the orientations of at least some bulges of adjacent webs, which lie substantially at the same height in the longitudinal direction are set against each other.
  • 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 of the two channel limiting webs lying at the same height facing away from each other bulges have, so that the channel width is increased by the bulges.
  • a slowdown of the flow can be achieved at this point.
  • an alternating widening 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 is effected 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 about 4 mm and 20 mm, particularly preferably between about 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, AIMn alloy, AlMg alloy and AIMgSi alloy.
  • Such light metal alloys are particularly readily extrudable and formable 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 tube diameter the high 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-section 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 (dh) 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 less than 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 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 full web is in a corresponding design preferably in a range between 0.5 and 1, 0, particularly preferably in a range between 0.6 and 0.8.
  • 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 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 50 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 are widely used, in particular, in motor vehicles, wherein 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 the features of claim 57 for a manufacturing method for the extrusion tube.
  • the extruded profiles are first formed in the manner of a consistently prismatic basic 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 process, 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 are opposite, wherein in the longitudinal direction of a channel a bulge of one of the side walls and a bulge of the web are alternately provided one behind the other, preferably in the longitudinal direction of a channel first 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, Subsequently, a bulge of the web in the respective other orientation and then a bulge of the other side wall, preferably in the longitudinal direction of a channel bulges of the channel delimiting two webs lying at the same height lying, oppositely directed bulges, so that the channel width reduced by the bulges is, preferably in the longitudinal direction of a channel bulges of the channel delimiting webs at the same height lying, away from each other directed bulges have, so that the channel width is increased by the bulges, wherein preferably the Forming of the web
  • the controlled-oriented bulging of the web is effected by means of a stamping tool inclined relative to the side walls, wherein preferably the controlled-oriented bulging of the web takes place by means of a stamping tool acting off-center relative to the web, wherein preferably one end-side region of the extruded tube does not coincide Buckling is provided, 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 is present, preferably in the bent portion at least partially no bulges are arranged, wherein preferably the tube material from one of the group aluminum alloy, AIMn 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, wherein preferably in the longitudinal 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
  • a rib element is arranged on at least one of the side walls from the outside, in particular by means of material connection, wherein a repeat unit of the embossments 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-way protrudes from one of the side walls in one of the channels.
  • a hydraulic diameter defined as four times the ratio of the area of the flow-through cross-section to a circumference wetted by the first fluid is in the range between 1.2 mm and 6 mm, the hydraulic diameter preferably being 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 is 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, wherein 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, wherein 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 carried out by means of an embossing roll, the embossing preferably being effected by means of an embossing stamp, the embossing preferably being followed by a step of severing the extruded tubes from an endless or quasi-free profile strand, the cutting preferably being effected by a sawing process or by a tear-off, in particular after a previous scoring takes place.
  • Fig. 1 shows a schematic representation of an extrusion tube for defining the individual spatial axes.
  • Fig. 2 shows a first embodiment of an extrusion tube according to the invention with a total of nine modifications 2.1 to 2.9.
  • FIG. 3 shows a representation of embossing processes for producing an extruded tube according to FIG. 2.
  • Fig. 4 shows a perspective view of an extruded tube according to the first embodiment.
  • FIG. 5 shows a section of the extruded tube according to FIG. 4.
  • Fig. 6 shows a second embodiment of an extrusion tube according to the invention with ten modifications 6.1 to 6.10.
  • Fig. 6a shows further modifications 6.11 to 6.15 of the second embodiment.
  • FIG. 7 shows three-dimensional views of two embossing rollers for producing an extrusion tube according to the invention.
  • FIG. Fig. 8 shows a measurement and calculation based on a preferred choice of a hydraulic diameter with respect to the ratio of the wettable by the first fluid circumference and an outer circumference of the extruded tube.
  • FIGS. 9A and 9B show two modifications of a preferred embodiment of a cross section of an extruded tube with an extruded channel jacket and webs extruded with the channel jacket.
  • FIGS. 10A and 10B show two modifications of a further embodiment as in FIGS. 9A and 9B with partial webs.
  • FIGS. 11A and 11B show two modifications of a further embodiment as in FIGS. 9A and 9B with partial webs.
  • Fig. 12 shows a further embodiment of a cross section of an extruded tube with partial webs.
  • FIG. 13 shows a further embodiment of a cross section of an extruded tube with partial webs.
  • 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 designated as y-direction in FIG. 1, wherein the (long) side walls 1, 2 of the extruded tube extend essentially in this direction.
  • a vertical direction is designated x in FIG. 1 and extends perpendicular to the longitudinal direction and to 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 at least one, in the embodiments shown, in each case a plurality of continuous webs 5, 79, 89 with the separation of mutually separate channels 6.
  • a plurality of continuous webs 5, 79, 89 with the separation of mutually separate channels 6.
  • optional part webs 5 ', 79' may also be provided (see, for example, FIG. 4 or also FIGS. 10A to 11B), 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 else bulges or buckles of the continuous webs 5, 79, 89, which protrude correspondingly 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.
  • an embossing punch 8 (see FIG. 3) or also an embossing roll 9 '(see FIG. 7) can have an inclined embossing edge 8a, 10'.
  • Fig. 3 a simple embossing of an extruded tube by means of a much of the extruding tube in the transverse direction covering, smooth and not inclined embossing edge is shown by A, by means of which the webs 5 uncontrollably bulged to the left or to the right.
  • the embossing edge is provided with an angle alpha of a few degrees, typically not more than ten degrees, relative to the side surface 1.
  • a check of the buckling direction can also be achieved for punctiform impressions.
  • a toothed embossing edge 8b is shown in the example C of FIG. 3, which 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 is given by the embossing roller 9 shown in Fig. 7 with point-like local projections 10.
  • the embossing roll 9 ' which is likewise shown in FIG. 7, has elongated projections 10' which extend over at least an entire channel width or over the substantially entire width of the extruded profile.
  • a roller 9 ' for example, embodiments such as those shown in Fig. 4 can be made, with the local projections of the embossing roller 9, embodiments as in Fig. 6 and Fig. 6a can be prepared.
  • the two types of projections 10, 10 ' can also be provided together on the same embossing roller.
  • first exemplary embodiment according to FIG. 2 and a second exemplary embodiment according to FIG. 6, each with a plurality of modifications, are essentially shown.
  • impressions of the first type with smooth, inclined embossing edges which at the same time overlap more than one web 5 of the extruded tube 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 opposing embossments may overlap (e.g., Fig. 2, Ex. 2.2, 2.4) or may be alternately staggered (e.g., 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 second embodiment of FIG. 6 are largely local impressions of the second type.
  • embossing is not carried out over the entire width of the tube, but only locally limited.
  • This has the advantage that the buckling of the pipe webs and the constriction of the channel height in the vertical direction can take place separately one after the other.
  • This results in an additional design flexibility, which is very helpful especially with regard to the generation of a swirling flow in the channels. In this way even more complex 3-dimensional vortex and flow conditions can be generated than in the first case.
  • 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 the buckling of a web 5 in the one direction by an indentation 7 on the upper side wall 1 an impression of the lower side wall 2, in the longitudinal direction following the buckling of a web 5 in the other orientation direction an impression 7 on the lower side wall 2 and in the longitudinal direction subsequently an impression 7 of the upper side wall 1.
  • cyclically repeats the expression of the webs by buckling of a web 5 in the first direction by an impression on the upper side wall 1 etc .. every several e other combinations and sequences of impressions in the flow direction is also conceivable, see exemplary representations 6.1 to 6.17 in Fig. 6 and 6a.
  • indentations of the side walls acting on the webs are in each case at least partially overlapping, so that the web is bulged at the same location starting from both side walls.
  • the direction of the bulge with respect to the overlapping indentations can be rectified (see about 6.11 and 6.13) or also directed in opposite directions (see 6.12).
  • FIG. 6 shows advantageous embossings by way of example on a tube with three intermediate webs 5.
  • the embossing of the upper side wall 1 is shown by a solid line and the embossing by the lower side wall 2 is shown by a dashed line.
  • 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.
  • indentations of the side walls 1, 2 are 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 °. Further arbitrary combinations between the direction of deflection and the order of impressions are also conceivable beyond the illustrated variants.
  • Examples 6.4, 6.5, 6.9 and 6.10 show variants with winglet-like, ie oblong and preferably angled embossings between the webs 5.
  • any combinations of the winglets with respect to one another are in relation to position as well as orientation to each other also to the direction of the webs 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-fold to 2.5-fold or about 2.5 times to 3.2 times.
  • impressions between the webs 5 in winglet shape have the advantage over simple molded embossings that even higher heat transfer performance can be achieved with this type of flow guidance, since the flow undergoes an even more directed deflection with a significantly 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.
  • the required distance of the profile end from the first embossing depends, in particular, 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 production process, first the embossing of the tubes and then the bending into the desired shape takes place.
  • the extrusion tube is embossed by means of at least one tool roll.
  • a roller 9 is exemplified.
  • at least two counter-rotating tool rolls are used, by which both the upper side wall 1 and the lower side wall 2 are embossed in one operation.
  • the extruded tube is stamped on a stamp set or various single dies.
  • 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 distance of the impressions is so large that a separation of the extruded tubes is possible.
  • the imprints are exposed at the separation point.
  • the latter can be provided for embossing by means of rolling, for example, by a corresponding geometry of the embossing die. In this case, 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 envelope, which occupies the desired embossing arrangement. In both cases, working with only one roller body.
  • the stamps in the sawing and joining area may need to be wholly or partially exposed to obtain a large sawing area, so that no or only very weak embossments are produced.
  • the extrusion tubes are either
  • the separation preferably takes place 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 charge air coolers, are all extrudable aluminum alloys, in particular Al alloys, in particular AIMn alloys, AlMg alloys and AlMgSi alloys.
  • the extrusion tube is in a corrosion-critical application, for example as a gas-carrying extruder tube of an exhaust gas cooler or a low pressure intercooler, corrosion tests have shown that that a particularly high corrosion resistance can be achieved by reducing impurities in the extruded material in the following proportions by mass:
  • Silicon Si ⁇ 1%, in particular Si ⁇ 0.6%, in particular Si ⁇ 0.15%
  • Iron Fe ⁇ 1.2% in particular Fe ⁇ 0.7%, in particular Fe ⁇ 0.35%
  • copper Cu ⁇ 0.5% in particular Cu ⁇ 0.2%, in particular Cu ⁇ 0.1% chromium Cr ⁇ 0.5%, in particular 0.05% ⁇ Cr ⁇ 0.25% , in particular
  • Titanium Ti ⁇ 0.5%, in particular 0.05% ⁇ Ti ⁇ 0.25%
  • 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.
  • the length of the embossing should in the case of the embodiment of FIG. 2 between 100% and 25% of the tube width, in particular between 90% and 35%, in particular in the range between 80% and 45% of the tube width.
  • the length of the indentation should in the case of the embodiment of Fig. 6 between 130% and 25% of the channel width, in particular between 90% and 35%, in particular in the range of 75% and 45% of the channel width.
  • the length of the embossment is in an embodiment not shown between 325% and 25% of the channel width, in particular between 250% and 35%, in particular in the range of 215% and 45% of the channel width.
  • intercooler For soldering on an external rib, eg for coolant radiator, intercooler: If an additional outer rib is applied to the embossed extruded tube, for instance in a crossflow cooler, care must be taken to ensure that the indentations in the transverse direction are not aligned, but slightly offset in order to ensure the best possible soldering of the outer rib.
  • the arrangements of impressions shown in FIGS. 2.3-2.9 and FIGS. 6.6-6. 10 are particularly suitable.
  • a hydraulic diameter has been found in a range between 2 mm and 5 mm.
  • a hydraulic diameter in the range between 3 mm and 3.4 mm, in particular between 3.1 mm and 3.3 mm proves to be particularly preferred.
  • a hydraulic diameter of about 3.2 mm is particularly useful.
  • 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 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 region has proved to be particularly expedient, in particular in the case of an extruded tube based on an aluminum material, in particular in the case of an extruded tube in which at least the channel jacket is based on an aluminum material.
  • 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 to be arranged in the pipe cross section, a web 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 extrusion tube having a hydraulic diameter according to the concept of the invention can thereby be realized.
  • 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.
  • a hydraulic diameter according to the concept of the invention can be realized in a particularly advantageous manner on the basis of an extruded flow channel.
  • 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 partial projections, in particular two opposite partial segments and / or two mutually offset partial segments lies at a height of the tube cross-section in a range below 0.8, preferably in a range from 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 illustrates the ratio of the circumference wetted by a fluid, such as exhaust gas, and an outer circumference of the extruding tube as a function of hydraulic diameter.
  • a preferred ratio results from the hatched areas of a preferred hydraulic diameter of 2 mm to 5 mm previously discussed , in particular 2.8 mm to 3.8 mm. From 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 given by way of example for a profile of an extruded tube which is specified in greater detail in FIG. 10B.
  • the ratio k should, as shown in FIG. 8 by arrows, be 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 as part of a high-pressure design in an exhaust gas recirculation system and to an exhaust gas cooler as part of a low-pressure configuration in an exhaust gas recirculation system.
  • FIGS. 9A to 11B are exemplary structural details of a cross section of different preferred extruded tubes.
  • FIGS. 9A and 9B show two modifications of an extrusion tube 61, 61 ', the modifications differing in that the shell thickness s in the extrusion tube 61' shown in FIG. 9B is thicker than a bridge thickness d, while that in FIG 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 an overall 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, which is given for the present extrusion tube 61, 61 'with reference to the distances a, b right below in Fig. 9B.
  • 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 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.
  • FIGS. 10A.2 and 10B.2 show two further modifications of a particularly preferred embodiment of an extrusion tube 71, 71 ', which differ - as explained above - 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, in addition thereto, partial webs 79' arranged alternately with the full 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.
  • the hydraulic diameter of the flow-through cross section in the extrusion tubes 71 shown in FIGS. 10A and 10B, 71 ' is indicated below Fig. 1OB.
  • 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 Each of the preferred extruded tubes shown in FIGS. 9A to 11B is provided according to the invention with embossments and bulges according to the illustrated exemplary embodiments, in order to optimize the turbulence and the heat transfer as well as the pressure drop in the specific application.
  • an embodiment with exclusive buckling of the solid and semi-webs is also advantageous. Due to the large number of webs and / or the length of the half-webs, an embossing of the pipe wall can lead to a blockage of the flow channel due to contacting or almost touching half-webs. Therefore, depending on the distance e, in particular for the profiles illustrated in FIGS. 10A, 10B and 11A, 11B, it is often more favorable to have only the webs and / or half webs buckled by specific impressions in the vicinity of the web extensions and Pipe walls only as little as possible. This is especially true for e ⁇ 1 / 3b.
  • FIGS. 12 and 13 each show further embodiments 91, 101 of cross sections of not yet bagged 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 of FIG. 13 at different heights.
  • the illustrations according to FIGS. 12 and 13 are true to scale, so that certain dimensional ratios of the drawn dimensions can be taken from them.

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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)

Abstract

L'invention concerne un tube filé pour échangeur de chaleur, comprenant deux parois latérales extérieures (1, 2) au moins sensiblement parallèles qui s'étendent dans une direction longitudinale (z) et une direction transversale (y) du tube filé, et qui sont reliées au moyen de deux petits côtés extérieurs (3, 4) dans une direction verticale (x) du tube filé, au moins une nervure continue (5) s'étendant entre les parois latérales (1, 2) en direction longitudinale (z) et en direction verticale (x) et séparant au moins deux canaux (6) du tube filé, au moins l'une des parois latérales extérieures (1, 2) présentant des empreintes (7), par l'intermédiaire desquelles sont formés des renflements (7) des parois latérales (1, 2) en saillie vers l'intérieur des canaux (6), ainsi que des renflements (7) de la nervure (5) s'étendant sensiblement en direction transversale (y). L'invention est caractérisée en ce que les renflements (7) d'au moins une nervure (5) présentent une orientation contrôlée par rapport à la direction transversale (y).
EP08869782.6A 2008-01-10 2008-12-18 Tube filé pour échangeur de chaleur Not-in-force EP2242979B1 (fr)

Applications Claiming Priority (2)

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

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

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US20110000657A1 (en) 2011-01-06
KR20100106434A (ko) 2010-10-01
CN101910774A (zh) 2010-12-08
EP2242979B1 (fr) 2014-09-24
DE102008062704A1 (de) 2009-08-27
WO2009086894A1 (fr) 2009-07-16
JP2011509393A (ja) 2011-03-24

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