EP1036296B1 - Flachrohr mit querversatz-umkehrbogenabschnitt und damit aufgebauter wärmeübertrager - Google Patents

Flachrohr mit querversatz-umkehrbogenabschnitt und damit aufgebauter wärmeübertrager Download PDF

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Publication number
EP1036296B1
EP1036296B1 EP99945947A EP99945947A EP1036296B1 EP 1036296 B1 EP1036296 B1 EP 1036296B1 EP 99945947 A EP99945947 A EP 99945947A EP 99945947 A EP99945947 A EP 99945947A EP 1036296 B1 EP1036296 B1 EP 1036296B1
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EP
European Patent Office
Prior art keywords
flat
pipe
flat tube
flat pipe
duct
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.)
Expired - Lifetime
Application number
EP99945947A
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German (de)
English (en)
French (fr)
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EP1036296A1 (de
Inventor
Bernd Dienhart
Hans-Joachim Krauss
Hagen Mittelstrass
Karl-Heinz Staffa
Christoph Walter
Jochen Schumm
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Ford Werke GmbH
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Ford Werke GmbH
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Publication date
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Publication of EP1036296A1 publication Critical patent/EP1036296A1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F28D1/0478—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • 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
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0085—Evaporators

Definitions

  • the invention relates to a flat tube according to the preamble of claim 1 and a flat tube heat exchanger according to the preamble of claim 5.
  • Flat tube type constructed tube block of this type are in the published patent application EP 0 659 500 A1.
  • the flat tube there becomes a straight flat tube blank first bent out of the flat tube plane in a U-shape, until the flat tube legs run parallel to each other, after which the latter by 90 ° with respect to the U-bend area be destroyed.
  • the resulting flat tube thus has two flat pipe sections lying in one plane, the ends of their mouths are on the same, the reversing arc section opposite side.
  • the angle, the flat tube transverse axis along the reverse bend section with the plane in which the straight pipe legs lie initially over one torsion area from zero to that at the top of the reverse arc section present value of 90 ° to then over the other Torsional range again to decrease to 0 °. therefore corresponds to the expansion of the flat tube perpendicular to the plane the flat pipe leg in the head area of the reversing bend section the flat tube width.
  • the heat exchanger tube block there are several such flat tubes in the direction stacked vertically to the plane of the straight flat tube legs, being because of in this direction the Width of the flat tubes corresponding expansion of the reversing bend sections the stack distance between the straight lines Pipe legs of adjacent flat tubes larger than the flat tube width must be kept.
  • the one-chamber design Flat tubes of the tube block open into one on one Side of the pipe block arranged by a collector Longitudinal partition is divided into two collection rooms, in which the flat tubes with one or the other End at the end.
  • a heat exchanger is in Serpentine construction reveals that with a tube fin block includes several serpentine, spiral flat tubes, which are stacked one on top of the other in the serpentine winding direction are.
  • the tube / fin block has in the Plane perpendicular to the pipe stacking direction a U-shape, each Serpentine flat tube with one end on each of the two free U ends in a respective, parallel to the stacking direction running manifold opens out.
  • the two ends each flat tube twisted by 90 °, and the two header tubes have corresponding, spaced apart Through slots in which the twisted pipe ends are recorded in a fluid-tight manner.
  • each serpentine flat tube in a side block area near one Serpentine turn twisted by 180 ° so that each flow channel of the multi-chamber flat tubes used into one Part of a block front and the other part of the opposite Block back is facing.
  • a heat exchanger disclosed with a tube / finned block containing a stack includes straight multi-chamber flat tubes attached to their both opposite ends at an angle of at most Are twisted at 45 ° and open into assigned manifolds, which correspond to their circumference in the longitudinal direction of the collecting tube spaced consecutive oblique slots are provided.
  • the invention is a technical problem of providing a flat tube of the type mentioned, which itself relatively easy to manufacture and very easy to build pressure-stable heat exchanger with low internal volume and high heat transfer efficiency, as well as one heat exchanger constructed from such flat tubes.
  • the invention solves this problem by providing it a flat tube with the features of claim 1 and one Heat exchanger with the features of claim 5.
  • the longitudinal direction is the plan through the course of the longitudinal axes Pipe sections defined while the stacking direction is one Direction indicates in which several flat tubes in the Formation of a heat exchanger tube block in succession to be ordered.
  • the transverse direction represents that to this Longitudinal direction and perpendicular to the stacking direction defined in this way Direction represents.
  • the transverse direction so defined parallel to the transverse axis direction of the flat pipe sections however, this is not mandatory, as the alternative plan pipe sections against this transverse direction if necessary can also be inclined.
  • the reverse sheet section Through this inventive design of the reverse sheet section it is achieved that its expansion in the stacking direction kept significantly smaller than the flat tube width can be. Accordingly, the spaces between need adjacent flat tubes when stacking a Rchrblocks from these flat tubes are not as large or larger than the flat tube width can be kept, but can be significantly narrower as to what makes a compact and pressure-stable heat exchanger favors.
  • the reverse bend section through relatively simple tube bending processes realize.
  • the flat tube can be used once or several times be bent in this way, its depth, i.e. its extent in the as defined above Transverse direction, enlarged with every bend. This leaves with relatively narrow, pressure-stable flat tubes an arbitrarily lower, i.e.
  • this transverse or depth direction usually the direction in which one closes Cooling or heating medium on the outside of the flat tube surfaces is passed through the heat exchanger.
  • the pipe gaps can be kept very narrow use correspondingly low heat-conducting corrugated fins, which is also the compactness and stability of a tube-fin block thus formed improved.
  • a flat tube developed according to claim 2 is bent over in such a way that the over a respective reverse arc section connected, flat pipe sections in the same or different, parallel to each other or against one another Predeterminable tilt angle inclined longitudinal planes, namely in any case preferably with a mutual distance in Cross direction between 0.2mm and 20mm.
  • flat tubes can be a Form a tube block with a depth that is twice the flat tube width plus the said distance between the plans Corresponds to pipe sections.
  • Flat tubes increase the tube block depth per reversing bend section by the flat tube width plus the said transverse distance of the flat pipe sections.
  • By leaving the Corresponding gaps are formed in a column with tube block constructed of such flat tubes, which e.g. in use an evaporator of a motor vehicle air conditioning system the condensation removal is facilitated.
  • Thermal fins can be continuous if necessary across the entire pipe block depth and also slightly above extend out.
  • flat tube Seraentine flat tube by at least one of the two Flat tube parts connected via a reversing bend section in the stacking direction is bent to a tubular serpentine, i.e. it consists of serpentine turns which follow one another in the stacking direction.
  • serpentine heat exchanger With flat tubes designed in this way, one can so-called serpentine heat exchanger with any Number of successive serpentine block parts in the depth direction build up.
  • the heat exchanger according to claim 5 is by use one or more of the flat tubes according to the invention under construction characterized a corresponding pipe block, with the above-mentioned properties and advantages of such Tube block construction.
  • the heat exchanger is both in single layer Construction in which the flat tube sections between two reversing bend sections or between a reverse arc section and a flat tube end made of a flat, straight tube section exist, as well as in serpentine construction, in which these flat tube sections to a coil are bent.
  • trained heat exchangers are the tube ends of the flat tubes and used hence the associated collection and distribution channels, below uniformly as collection channels for the sake of simplicity designated, on opposite sides of the pipe block.
  • the collecting channels can then from a collecting box or collecting pipe be formed on the relevant tube block side along the stacking direction, also referred to as the block vertical direction run and the parallel feed or discharge of the tempering medium passed through the inside of the pipe serve or from the individual flat tubes.
  • the flat tube ends all on the same Tube block side. Due to the design of the flat tubes are the two tube ends of each flat tube to each other offset in the block depth direction so that they two correspondingly adjacent to each other in the block depth direction Known collection channels. To be done accordingly Inlet and outlet of the piped through the interior of the pipe Temperature control medium on the same heat exchanger side.
  • this type of heat exchanger with two side-by-side collecting channels on the same tube block side is provided according to claim 8, these collecting channels through two separate header pipes or header boxes, below
  • manifolds or to form through a common manifold.
  • the latter can be realized in that a first uniform manifold interior with a longitudinal partition in the two collecting channels is divided, or in that the Collecting tube as an extruded tube profile with two separate, the hollow chambers forming the collecting channels is manufactured.
  • heat exchanger is at least one of the two manifolds or at least one of the two hollow chambers of a longitudinally divided manifold through transverse partition walls in several, in the vertical direction from each other separate collection channels divided.
  • This will make one serial flow through the flat tubes in the tube block achieved by the tube block via a first collecting channel of the cross-divided manifold or the cross-divided Cavity medium supplied initially only in the part of all of the flat tubes opening there is fed.
  • the Collecting channel in which this part of the flat tubes with the other Pipe end opens, then acts as a deflection channel in which the temperature control medium from the flat pipes opening there in another, also ending there with one end Part of all flat tubes is deflected.
  • Number and location of the Cross partitions determine the division of the flat tubes into successive groups of parallel flows Flat tubes.
  • the flat tube 1 shown in a top view in FIG. 1 is made in one piece from a straight multi-chamber profile using suitable bending processes manufactured. It contains two flat, straight pipe sections 2a, 2b, which over a reverse arc section 3 are connected to each other and opposite Flow directions for one through the several parallel chambers tempering medium passed through inside the flat tube 1, e.g. have a refrigerant of a vehicle air conditioner.
  • One of both potential Flow profiles is in Fig. 1 by corresponding flow arrows 4a, 4b.
  • the parallel to the flow directions 4a, 4b longitudinal axes 5a, 5b of the two plan define straight pipe sections 2a, 2b a longitudinal direction x and are perpendicular to it Transverse direction y offset from each other.
  • both are plan pipe sections 2a, 2b in a common xy plane, which is perpendicular to a stacking direction z, in which several such flat tubes to form a heat exchanger tube block can be stacked on top of each other as shown below using the 3 and 4 explained in more detail.
  • the corresponding coordinate axes x, y, z shown.
  • the reversing sheet section 3 is obtained by the fact that the initial rectilinear flat tube profile of a desired Width b held at half its length and both tube halves are each turned at a 90 ° angle so that they are parallel to each other perpendicular to their original Run longitudinally and in this way the two straight lines Form tube sections 2a, 2b of the finished flat tube 1.
  • the bending process takes place in such a way that the two rectilinear pipe sections 2a, 2b lying in one plane with a distance a that can be selected depending on the application, which is preferably between about 0.2 mm and 20 mm, while the flat tube width b is typically between one and a few centimeters.
  • the killing takes place alternatively about the respective longitudinal central axis 5a, 5b also about a parallel longitudinal axis, i.e. with a transverse offset with respect to the longitudinal central axis, around any one Angle between 0 ° and 90 °, in the case shown the torsion angle is approximately 60 °, as is particularly clear from FIG. 4 can be seen.
  • FIG. 3 and 4 show an application for the flat tube type 1 and 2 in the form of a tube / fin block Evaporator, as used in particular in automotive air conditioning systems is usable. It is understood that the Sectional heat exchangers shown depending on the design can also be used for any other heat transfer purposes leaves. As can be seen from FIG. 3, this contains an evaporator a stack between two end cover plates 9, 10 several flat tubes 1 according to FIGS. 1 and 2 with intermediate, heat-conducting corrugated fins 8. The height of the heat-conducting fins 8 corresponds approximately to the height c of the flat tube reversing bend sections 3 and is therefore significantly smaller than the flat tube width b.
  • the use 1 and 2 a tube-fin block with in depth, i.e. in the y direction, two-part structure formed, with in each of the two block parts Pipe sections with the same flow direction in the Stack direction z one above the other.
  • Between the two Block parts is the distance a between the two straight lines Pipe sections 2a, 2b corresponding to each flat tube 1 Gap formed.
  • the corrugated ribs 8 extend in one piece over the entire flat tube depth and thus also over this Gap, being on both sides, i.e. at the Survive front and back of the block as needed can.
  • the block front is defined here that they are from an outside over the evaporator surfaces conducted away second temperature control medium, e.g. to cooling supply air for a vehicle interior, in the pipe transverse direction y, i.e. in the depth direction of the block.
  • the transverse extent d the flat tube ends are less due to their twisting than the flat tube width b.
  • a common manifold for Both stack rows of the tube ends 6a, 6b may be provided by means of a longitudinal partition into the two required, separate ones Collection channels is divided.
  • the one shown in the example Twisting the pipe ends by approx. 60 ° enables that relatively close succession of the single-layer flat tubes 1 in Stack with the said, compared to the flat tube width b smaller Stack height c is not hindered.
  • the evaporator with the tube / fin block thus formed in a compact design and very pressure-stable and has a high heat transfer efficiency having.
  • a heat transfer performance are achieved for the otherwise at least about twice so wide, not bent flat tubes would be required.
  • the unique flat tube deflection means that that the tempering medium to be passed through the tube interior fed in and out on one and the same tube block side can be, which is advantageous in some applications is.
  • 5 and 6 is an embodiment in a serpentine construction shown.
  • 5 shows the detail view thereby one of several serpentine flat tubes 11, which for Formation of the serpentine tube block there in any desired Number are stacked.
  • the one used for this Serpentine flat tube 11 is largely identical to that of FIGS. 1 and 2, with the exception that on both sides of the same as that of FIGS. 1 and 2 reversing arc section 3 'not just a straight line, single-layer pipe section, but a multiple serpentine convoluted coil section 12a, 12b connects, which in turn is a corresponding one in the block depth direction Face the gap offset, as in FIG. 6 can be seen more clearly.
  • each Pipe section 12a, 12b are through as usual Bend the flat tube at the relevant point around the pipe transverse axis formed there by an angle of 180 °.
  • Between the individual coils 13 and between successive serpentine flat tubes 11 are thermally conductive Corrugated ribs 14 continuously from the block front to. Block back introduced with optional overhang.
  • a row of corrugated ribs for each of the two pipe block rows offset in the block depth direction are provided can be, in which case the gap between the two rows of blocks can remain free.
  • the height of the thermal fins 14 and thus the Stack spacing between adjacent, straight flat tube sections both within a serpentine flat tube 11 as well approximately between two neighboring seroentine flat tubes the significantly lower height than the flat tube width b c of the reverse arc section 3 '.
  • the serpentine evaporator 5 and 6 In contrast to the evaporator in single-layer flat tube construction 3 and 4 is the serpentine evaporator 5 and 6 the reversing arc section 3 ' on the same tube block side as the twisted tube ends 15a, 15b.
  • the serpentine coils 13 impede the successive ones in the stacking direction twisted pipe ends 15a, 15b and reverse bend sections 3 'not.
  • the flat tube can be two or more turnaround sections and corresponding diversions exhibit.
  • An example with two consecutive reverse arc sections 17, 18 is schematic based on the associated Flow path shown in Fig. 7. From one Flat tube end 19 extends a first straight tube section 20 to the opposite first reverse arc section 17, where he is returning to a second rectilinear Flat tube section 21 merges with the opposite one second reversing arc section 18 into a third rectilinear pipe section 22 passes over to the other Flat tube end 23 extends.
  • This flat tube is suitable thus building a three-part block depth Heat exchanger tube blocks in single-layer construction, i.e. the rectilinear pipe sections 20, 21, 22 are essentially in a block level.
  • the two ends 19, 23 each Flat tubes open on opposite sides of the block which must therefore each be arranged with a manifold.
  • possible reverse arc section comes an additional straight line Flat tube section added in the block depth direction, and in addition the position of the one changes to the other Flat tube end and thus the positioning of the two associated Collection channels between an equilateral and an opposite position.
  • the serpentine flat tube can also be used in a corresponding manner 11 of Fig. 5 are modified so that by at least another serpentine turn in one and / or in other serpentine pipe section the relevant flat pipe end on the block side opposite to the reversing arch section comes to rest.
  • a serpentine flat tube of the type of Fig. 5 but with a or several additional reversing arc sections are provided to be analogous to e.g. 7 in the block depth direction at least three-part pipe block for one To build serpentine heat exchangers.
  • the flat tube ends can also be left undetected.
  • a two-chamber manifold can be used, which already in the production stage, two separate, longitudinal hollow chambers having.
  • Such a manifold 24 is in cross section shown in Fig. 8. It is extruded from one Profile manufactured and integrally includes two separate Longitudinal chambers 25, 26, which are the collecting channels for the form the relevant heat exchanger.
  • the several by means of appropriate transverse walls, in the Block vertical direction z contain separate collecting channels.
  • the flat tubes in the tube block become several Groups combined in such a way that the pipes of a group flows in parallel and flows through the various tube groups in series become.
  • a supplied tempering medium flows from one inlet-side collecting channel into the group of those opening there Flat tubes and then gets in at their other end a collecting duct that acts as a deflection space, into which a second flat tube group opens in addition to this first group, into which the temperature control medium is then deflected.
  • This can be done by appropriate Position the cross walls in one or both header pipes be continued in any way up to an outlet-side collecting channel, through which the temperature control medium then leaves the tube block.
  • the flat tubes according to the invention can be used to produce very compact, pressure-stable flat tube blocks in a single-layer construction or serpentine construction with a high heat transfer capacity.
  • Heat exchangers produced in this way are also suitable, for example, for CO 2 air conditioning systems operating at comparatively high pressure, as are increasingly being considered for motor vehicles.
  • FIGS. 9 and 10 The illustration of the reversing arch section (3) from FIG. 1 is shown in FIGS. 9 and 10 technically precise. In particular, it must be made clear that the Flat tube transverse axis in the area of the reversing bend section (3) of a straight line equivalent.
  • the flat tube is bent along a straight line (G1) at an angle of 45 ° to the longitudinal axis (5) of the Flat tube and deflected at a right angle with respect to the longitudinal axis (5), and after another redirection at an angle of 90 ° with respect to the longitudinal axis (5) the flat tube then runs in the opposite direction from the Reverse arc section (3) out.
  • the resulting outer contour is characterized by the angle of 45 °, with which in the top view according to FIG. 9 shows the bending edge (G1) in relation to Longitudinal axis (5) can be represented.
  • FIG. 10 shows the side view of the flat tube, which is the view of the left part of FIG. 2 corresponds.
  • the angle in Reverse arc section designated ⁇ 1, the size of 0 °. This corresponds to the Parallel shift by bending and another parallel shift after Another bend in the plane of the original flat tube cross section (7).
  • the resulting height C1 is practically the minimum according to the invention double the thickness of the flat tube.
  • FIG Reversing arc section 3.2 The representation of an angle ⁇ 2 lying between ⁇ 1 and ⁇ 3 is shown in FIG Reversing arc section 3.2 outlines, the contour line U2 being less strong is curved as the contour line U3, but does not represent a straight line like that Contour line U1. 10, the height c2 is between the height C1 and the C3 level.
  • the Top view in Fig. 9 clearly shows that strictly speaking, the contours in top view in the area of the reversing arc section 3 each represent straight lines which are clear and can be clearly characterized by their angle to a plane.
  • FIG. 9 follows the theoretical idea that during the molding process of the reversing arch section (3) a torsion-like deformation around that in FIG. 9 shown inner contour line of the flat tube is executed. If you look at that resulting geometry differentially, the flat tube transverse axis (7) always remains one Just.
  • the angle of the straight line or the flat tube transverse axis (7) can thus be correct Determine the x / y plane (2a, b) at any time. It can also be formulated correctly under the theoretical assumption of the flat tube transverse axis (7) as the straight line Angle of any differential flat tube transverse axis (7) exactly to one Stack direction z vertical plane in the specified angular range from 0 to Determine 45 °.
  • the flat tubes according to the invention can be used to produce very compact, pressure-stable flat tube blocks in a single-layer construction or serpentine construction with a high heat transfer capacity.
  • Heat exchangers produced in this way are also suitable, for example, for CO 2 air conditioning systems operating at comparatively high pressure, as are increasingly being considered for motor vehicles.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP99945947A 1998-07-10 1999-07-09 Flachrohr mit querversatz-umkehrbogenabschnitt und damit aufgebauter wärmeübertrager Expired - Lifetime EP1036296B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19830863 1998-07-10
DE19830863A DE19830863A1 (de) 1998-07-10 1998-07-10 Flachrohr mit Querversatz-Umkehrbogenabschnitt und damit aufgebauter Wärmeübertrager
PCT/DE1999/002125 WO2000003190A1 (de) 1998-07-10 1999-07-09 Flachrohr mit querversatz-umkehrbogenabschnitt und damit aufgebauter wärmeübertrager

Publications (2)

Publication Number Publication Date
EP1036296A1 EP1036296A1 (de) 2000-09-20
EP1036296B1 true EP1036296B1 (de) 2004-01-02

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EP99945947A Expired - Lifetime EP1036296B1 (de) 1998-07-10 1999-07-09 Flachrohr mit querversatz-umkehrbogenabschnitt und damit aufgebauter wärmeübertrager

Country Status (6)

Country Link
US (1) US6546999B1 (ja)
EP (1) EP1036296B1 (ja)
JP (1) JP2002520570A (ja)
AU (1) AU5849199A (ja)
DE (1) DE19830863A1 (ja)
WO (1) WO2000003190A1 (ja)

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Publication number Priority date Publication date Assignee Title
DE102006018688A1 (de) * 2006-04-13 2007-10-18 Visteon Global Technologies Inc., Van Buren Verfahren zum Biegen von Flachrohren für Wärmeübertrager und gebogenes Flachrohr
DE102009047620C5 (de) 2009-12-08 2023-01-19 Hanon Systems Wärmeübertrager mit Rohrbündel

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DE10146824A1 (de) * 2001-09-18 2003-04-24 Behr Gmbh & Co Wärmeübertrager-Flachrohrblock mit umgeformten Flachrohrenden
WO2003040640A1 (fr) * 2001-11-08 2003-05-15 Zexel Valeo Climate Control Corporation Echangeur thermique et tube pour echangeur thermique
US20030102113A1 (en) * 2001-11-30 2003-06-05 Stephen Memory Heat exchanger for providing supercritical cooling of a working fluid in a transcritical cooling cycle
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JP2002520570A (ja) 2002-07-09
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EP1036296A1 (de) 2000-09-20
US6546999B1 (en) 2003-04-15
DE19830863A1 (de) 2000-01-13

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