WO2004074756A2 - Tube plat presentant une section coudee en u et echangeur thermique comportant un tel tube plat - Google Patents

Tube plat presentant une section coudee en u et echangeur thermique comportant un tel tube plat Download PDF

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Publication number
WO2004074756A2
WO2004074756A2 PCT/EP2004/001257 EP2004001257W WO2004074756A2 WO 2004074756 A2 WO2004074756 A2 WO 2004074756A2 EP 2004001257 W EP2004001257 W EP 2004001257W WO 2004074756 A2 WO2004074756 A2 WO 2004074756A2
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WO
WIPO (PCT)
Prior art keywords
flat tube
tube
flat
section
bend section
Prior art date
Application number
PCT/EP2004/001257
Other languages
German (de)
English (en)
Other versions
WO2004074756A3 (fr
Inventor
Walter Demuth
Wolfgang Geiger
Martin Kotsch
Michael Kranich
Karl-Heinz Staffa
Christoph Walter
Original Assignee
Behr Gmbh & 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 & Co. Kg filed Critical Behr Gmbh & Co. Kg
Priority to US10/545,889 priority Critical patent/US20060243432A1/en
Priority to BRPI0407582-0A priority patent/BRPI0407582A/pt
Priority to EP04710027A priority patent/EP1597529B1/fr
Priority to DE502004004288T priority patent/DE502004004288D1/de
Priority to JP2006501805A priority patent/JP2006518029A/ja
Publication of WO2004074756A2 publication Critical patent/WO2004074756A2/fr
Publication of WO2004074756A3 publication Critical patent/WO2004074756A3/fr

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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
    • F28D1/0475—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
    • 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
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers

Definitions

  • the invention relates to a flat tube according to the preamble of claim 1 and to a heat exchanger constructed therewith.
  • a generic flat tube with an inverted bend section and a heat exchanger with a tube block constructed from this type of flat tube are described in the published patent application DE 198 30 863 A1.
  • the flat tube is bent over in such a way that its two adjacent, flat tube sections run in the longitudinal direction with opposite flow directions and with longitudinal axes offset at least in the transverse direction.
  • the published patent application EP 0 659 500 A1 likewise describes a flat tube with a reversing bend section and a heat exchanger with a tube block constructed from this type of flat tube.
  • a straight flat tube blank is first bent out of the flat tube plane in a U-shape until the flat tube legs run parallel to one another, after which the latter are each 90 ° with respect to the U- Bow area are twisted.
  • the resulting flat tube thus has two flat tube sections lying in one plane, the ends of which end on the same side opposite the reversing bend section.
  • the angle which the flat tube transverse axis encloses along the reversing bend section with the plane in which the straight pipe legs lie initially increases over one torsion range from zero to the value of 90 ° present at the head end of the reversing bend section, and then over the other Torsional range again to decrease to 0 °.
  • a disadvantage of the described reversing bend section is that the extension of the flat tube perpendicular to the plane of the flat pipe legs in the head region of the reversing bend section always corresponds to a flat tube width and therefore cannot be reduced if necessary, so that the dimensions of the associated heat exchanger tube block in the direction perpendicular to the plane of the straight flat tube legs cannot be influenced.
  • the object of the invention is to provide a flat tube with an inverted bend section which is relatively simple to manufacture and is suitable for building very pressure-stable heat exchangers with a small installation space, and to provide a heat exchanger constructed from such flat tubes.
  • the main idea of the invention is to form a reversing arc section such that a main bending axis is parallel to the Flat tube plane and runs at a predeterminable angle to the pipe longitudinal extension, the flat pipe plane being determined by the length and width of the flat pipe.
  • a predeterminable angle to the pipe longitudinal extension is 90 °, ie, the main bending axis is perpendicular to the longitudinal tube extension.
  • the flat tube according to the invention is displaced in the area of the reversing bend section in the flat tube plane parallel to the tube extension by a path s, the path s being composed of a flat tube width b and a desired distance d between the flat tube sections after the forming.
  • an angle ⁇ with which the flat tube sections pass into the reversing bend section can be freely selected during the shaping of the flat tubes and, in an advantageous embodiment of the invention, is in the range of 13 ° ⁇ ⁇ 67 °.
  • the angle ⁇ and / or the path s is achieved by at least one bending operation about at least one bending axis (B) which is perpendicular to the flat tube plane.
  • the displacement of the flat tube is achieved by two bending processes about two bending axes, which are carried out before or after the main bending process about the first bending axis, the first bending axis running in the middle of the offset area, the offset area being approximately twice is as long as the reverse arc section.
  • the two planar tube sections adjoining the reversing bend section are arranged lying parallel to the stacking direction z, preferably with one, in parallel planes laterally offset from one another after the shaping process
  • a tube block in a serpentine construction can be formed, in which the serpentines are laterally offset.
  • the tube block thus formed has a depth of twice the flat tube width plus the said distance d between the flat tube sections.
  • the tube block depth per reversing bend section increases by the flat tube width plus the said transverse distance d of the flat tube sections. Due to the transverse spacing, corresponding gaps form between the flat tube sections in a tube block constructed with such flat tubes, which facilitates the condensation removal, e.g. in the application of the pipe block in an evaporator of a motor vehicle air conditioning system.
  • the reversing bend section is formed in a further shaping step such that the two tube sections lie next to one another and parallel with the distance d in a common plane. This can be done by symmetrical or asymmetrical shaping of the reversing arch section.
  • Flat tube sections are in the same plane - referred to below as the first reversing bend sections - and the reversing bend sections in which the flat tubes are located in different planes - hereinafter referred to as designated second reversing bend sections -, a tube block in serpentine construction can be realized, the depth of which depends on the number of first reversing bend sections formed in succession.
  • a pipe block in a serpentine construction with a depth of twice the flat pipe width plus the said distance d between the flat pipe sections can be realized, in which a tempering medium , for example a refrigerant or a coolant, first flows through the flat tube sections which lie in a common plane, and then flows through the flat tube sections which lie in the stacking direction or counter to the stacking direction in the next common plane.
  • a tempering medium for example a refrigerant or a coolant
  • a serpentine design by executing a number of second reversing arch sections without lateral offset - hereinafter referred to as the third reversing arch section - for example in the stacking direction, and then forming a first reversing arch section, to which a number of Connect the second reverse bend sections.
  • a second reversing arc section can of course also be arranged.
  • the main bending process around the main bending axis is carried out at a predeterminable angle to the longitudinal pipe extension, the predeterminable angle essentially corresponding to the angle ⁇ with which the flat pipe sections merge into the reversing bend section.
  • the two flat tube sections lie in two mutually parallel planes, the two flat tube sections enclosing an angle with a value of 2 ⁇ .
  • the two pipe legs are each deformed with a further bending process about a bending axis that runs perpendicular to the flat pipe plane, so that they each transition into the reversing bend section at the angle ⁇ .
  • the described procedure provides the required already described offset of the flat tube in a different way.
  • the further forming steps are carried out analogously to those already described in order to ensure that the two flat tube sections lie next to one another and parallel with the distance d in a common plane. As already stated, this can be done by symmetrical or asymmetrical shaping of the reversing arch section.
  • the gaps between adjacent flat tubes do not need to be kept as large or not larger than the flat tube width when stacking a tube block from these flat tubes, but can be significantly narrower, which favors the production of a compact and pressure-stable heat exchanger.
  • the reverse bend section can be realized by relatively simple pipe bending processes.
  • the flat tube can be bent one or more times in this way, its depth, ie its extent in the transverse direction as defined above, increasing with each bend if the lateral offset is always in the same direction.
  • a tube block of any depth, that is to say expanding in the transverse direction can be formed, this transverse or depth direction usually representing the direction in which a medium to be cooled or heated is passed outside through the flat tube surfaces through the Heat exchanger is passed through.
  • Additional heat-conducting fins are usually provided between the tube block sections which follow one another in the stacking direction in order to improve the heat transfer. Since, as already mentioned, the tube interspaces can be kept very narrow, correspondingly low heat-conducting corrugated fins can also be used, which likewise improves the compactness and stability of a tube / fin block formed in this way.
  • a flat tube heat exchanger for motor vehicle air conditioning systems several flat tubes according to the invention are stacked one above the other in the stacking direction z to form a tube block.
  • the flat tubes each end with one end in at least one laterally arranged collecting channel running in the stacking direction of the tube block, at least one of the two tube sections connected to one another via the reversing bend section can form a tubular serpentine wound in the stacking direction z, and wherein the two flat tube ends lie on the same or on opposite sides and at least one of the two tube ends can be twisted by an angle between 0 ° and 90 °.
  • the flat tubes according to the invention By designing the flat tubes according to the invention with a 180 ° deflection in the flow direction, it is possible to realize a smaller installation space for the heat exchangers, such as a gas cooler or an evaporator, since closer distances in the stacking direction and / or between the tubes can be achieved. In addition, springing up of the flat tube legs is almost avoided. Another advantage is that the heat exchangers constructed with the flat tubes according to the invention have a stiffer construction with tighter tolerances.
  • the refrigerant is led to the air in a cross-countercurrent flow.
  • the flat tube runs back in the same plane as on the outward path, but offset laterally by a path s, so that the leading section of the flat tube from the returning section by a distance d is distant.
  • the two flat tube sections lie in the same plane, which is determined by the length and width of the flat tubes in their straight sections.
  • the forming is preferably carried out in three stages. In the first stage, the flat tube experiences a lateral offset from the stretched state. The amount of the offset s corresponds to the sum of the flat tube width b and the distance d.
  • a bend with a radius r around a main bending axis A parallel to the flat tube plane and perpendicular to the tube extension, where r is the inner radius of the bend.
  • the main bending axis A lies approximately in the middle of the offset area.
  • the sections of the flat tube are then parallel to each other in different planes.
  • the reverse arc section is formed that the flat tube sections are again in a common plane.
  • the deformed reversing bend section can either be completely below or above with respect to the common flat tube plane or be symmetrical with respect to this common plane.
  • any asymmetrical positions of the reversing arch section to the common plane are possible.
  • the forming steps can also be interchanged.
  • the flat tube according to the invention forms a serpentine flat tube, in that at least one of the two flat tube sections connected via a reversing bend section is bent in the stacking direction to form a pipe serpentine, ie it consists of third reversing bend sections successively in the stacking direction with the corresponding flat pipe sections.
  • a so-called serpentine heat exchanger can be constructed with any number of serpentine block parts which follow one another in the depth direction.
  • the mouth ends lie on the same or on opposite sides, with at least one end, preferably both ends, being twisted in relation to the subsequent central region.
  • This twisting rotates the flat tube transverse axis in the direction of the mouth end towards the stacking direction, so that the extension of the flat tube ends in the transverse direction can be kept smaller than the flat tube width.
  • the twisting takes place at a maximum of 90 °, so that in the case of flat pipe sections running perpendicular to the stacking direction, the pipe ends are parallel to the stacking direction and their extent in the transverse direction is only as large as the flat pipe thickness. This enables a comparatively close arrangement of associated pipe block in the depth direction of a pipe block constructed therewith, on the relevant pipe block side in the stacking direction, extending collection and distribution channels.
  • a heat exchanger is characterized by the use of one or more of the flat tubes according to the invention in the construction of a corresponding tube block, with the above-mentioned properties and advantages of such a tube block structure.
  • a compact, highly pressure-stable evaporator with a relatively low weight, low internal volume and good condensate separation for an air conditioning system of a motor vehicle can be realized in this way, multi-chamber flat tubes preferably being used.
  • the heat exchanger can be implemented in a single-layer construction, in which the flat tube sections between two reversing bend sections or between a reversing bend section and a flat tube end consist of a flat, straight tube section, and in a serpentine construction, in which these flat tube sections are bent into a coil.
  • the tube ends of the flat tubes used and thus also the associated collecting and distribution channels are located on opposite sides of the tube block.
  • the collecting channels can then each be formed by a collecting box or collecting pipe, which run along the stacking direction on the relevant pipe block side, also referred to as the block vertical direction, and the parallel supply or discharge of the temperature control medium passed through the pipe interior to and from the individual flat pipes serve.
  • the flat tube ends all open on the same tube block side. Due to the design of the flat tubes, the two tube ends of each flat tube are offset from one another in the direction of the block depth, so that two corresponding collecting channels lying adjacent to one another in the direction of the block depth can be assigned to them. Accordingly, the temperature control medium passed through the interior of the pipe is supplied and removed on the same heat exchanger side.
  • these collecting channels are formed by two separate collecting pipes or collecting boxes, hereinafter referred to simply as collecting pipes for the sake of simplicity, or by a common collecting pipe.
  • the latter can be achieved by dividing an initially uniform collecting tube interior with a longitudinal partition into the two collecting channels, or by producing the collecting tube as an extruded tube profile with two separate hollow chambers forming the collecting channels.
  • At least one of the two manifolds or at least one of the two hollow chambers is one longitudinally divided collecting pipe divided by transverse partition walls into several collecting channels separated from each other in the block vertical direction.
  • Temperature control medium is initially only fed into the part of all flat tubes that opens there.
  • the number and position of the transverse partition walls determine the division of the flat tubes into successively flowed through groups of parallel flowed flat tubes.
  • the arrangement of the flat tubes with respect to an air flow remains unchanged despite the reversing bend section, i. H. one side of the flat tube facing the air continues to face the air after the reversing bend section and one side of the flat tube facing away from the air continues to face away from the air even after the reversing bend section.
  • Figure 1 is a plan view of a flat tube with a reverse bend section and twisted tube ends.
  • 3a shows a plan view of a flat tube before a bending process about a main bending axis A
  • 3b shows a plan view of a flat tube after a bending process about a main bending axis A
  • FIGS. 4 is a partial side view of a tube / fin block of a heat exchanger constructed from flat tubes according to FIGS. 1 and 2,
  • FIG. 5 is a partial side view of a tube / fin block of a heat exchanger with serpentine 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. It includes two flat, rectilinear pipe sections 2a, 2b, which are connected to one another via an inverted bend section 3 and have opposite flow directions for a temperature control medium passed through the several parallel chambers inside the flat pipe 1, for example a refrigerant of a motor vehicle air conditioning system.
  • a temperature control medium passed through the several parallel chambers inside the flat pipe 1, for example a refrigerant of a motor vehicle air conditioning system.
  • One of the two possible flow profiles is shown in FIG. 1 by corresponding flow arrows 4a, 4b.
  • the longitudinal axes 5a, 5b of the two running parallel to the flow directions 4a, 4b plane, straight pipe sections 2a, 2b define a longitudinal direction x and are offset from one another in a transverse direction y perpendicular thereto.
  • the two flat tube sections 2a, 2b lie with a first reversing arc section 3 in a common xy plane, which is perpendicular to a stacking direction z, in which several such flat tubes are used
  • Formation of a heat exchanger tube block can be stacked on top of one another, as will be explained in more detail below with reference to FIGS. 4 and 5.
  • the corresponding coordinate axes x, y, z are shown in FIGS. 1 to 5.
  • the reversing bend section 3 is obtained in that the initial, rectilinear flat tube profile of a desired width b is shifted in the area of an offset region U as shown in FIG. 3a in the flat tube plane parallel to the tube extension by a path s which is determined by the tube width b and the desired one Distance d is composed.
  • the shift or the offset can take place in the positive y direction or in the opposite direction in the negative y direction.
  • the transition between the flat tube sections 2a, 2b and the reversing bend section 3 takes place at a predeterminable angle ⁇ .
  • the angle ⁇ and / or the path s are achieved by at least one bending process around at least one bending axis B1, B2, which runs perpendicular to the flat tube plane.
  • the described offset by the path s is preferably achieved by two bending processes around the bending axes B1 and B2 shown in FIG. 3a, these two bending processes preferably being carried out before the bending process around the main bending axis A.
  • the main bending axis A runs in the middle of the offset area U, the offset area U being approximately twice as long as the reversing arc section 3.
  • the two straight tube sections 2a, 2b of the flat tube 1 are obtained.
  • the two straight pipe sections 2a, 2b are offset, as shown in FIG. 2a, in mutually parallel planes with a selectable distance 2r in the z direction and in the selectable distance d in the y direction, the following applies to the maximum inner radius r: ( h r d FR ) / 2, where h r is the height of the fins and d F is the flat tube thickness, which results in a reasonable lower limit for r the flat tube thickness d FR .
  • a reasonable value for the angle ⁇ lies within the limits 13 ° ⁇ ⁇ 67 °.
  • the selectable distance is preferably between approximately 0.2 mm and 20 mm, while the flat tube width b is typically between one and a few centimeters.
  • straight pipe sections 2a, 2b are connected to one another on the one side via the reversing bend section 3, they both run out on the opposite side in the form of twisted pipe ends 6a, 6b.
  • the twisting takes place about the respective longitudinal central axis 5a, 5b, alternatively also about a parallel longitudinal axis, i.e. with a transverse offset with respect to the longitudinal central axis, by an arbitrary angle between 0 ° and 90 °, the torsion angle being approximately 90 ° in the case shown.
  • FIG. 2 it is clear that due to the described formation of the reversing sheet section 3, the height c of the reversing sheet section 3 and thus the extent in the stacking direction z is small and can be selected depending on the bending radius. In particular, this height c of the reversing bend section 3 remains significantly smaller than the flat tube width b. As a result, several such flat tubes can be stacked on top of one another in a heat exchanger tube block with a stack height that can be kept significantly smaller than the flat tube width, as the heat exchanger examples described below show.
  • a further modification of the flat tube of FIGS. 1 and 2 may consist in the fact that the two flat tube sections 2a, 2b lie in two mutually offset xy planes, as shown in FIG. 2a.
  • the transverse direction y is defined by the fact that it is both for Longitudinal direction x of the straight pipe sections and perpendicular to the pipe block stacking direction z.
  • FIG. 3b shows an alternative possibility for designing the reversing sheet section 3 after a main bending process.
  • the main bending process around the bending axis A is carried out here before the offset is realized by further bending processes around a bending axis B3.
  • the main bending axis A runs at the predeterminable angle ⁇ in the limits 13 ° ⁇ ⁇ 67 ° to the pipe longitudinal extension.
  • the two pipe sections are each bent inwards about the bending axis 3 according to the arrows. According to the illustration in FIG.
  • the distance d between the flat tubes is realized by a limitation, in the example shown realized by a limitation bar with the width d, the bending axis B3 being implemented by an upper end of the limitation bar in the example shown.
  • the flat tube sections 2a and 2b shown lie in different parallel planes and include a diaper of 2. After the additional bending processes, the two flat tube sections 2a and 2b lie parallel to one another in the different parallel planes, as shown in FIG. 2a, so that the further shaping steps already described can be carried out in order to ensure that the two flat tube sections 2a, 2b are parallel with each other the distance d lie in a common plane (see FIGS. 2b to 2c).
  • FIGS. 4 and 5 show an application for the flat tube type of FIGS. 1 and 2 in the form of a tube / fin block 9 of an evaporator 10, as can be used in particular in motor vehicle air conditioning systems.
  • the heat exchanger shown in sections can also be used for any other heat transfer purposes, for example as a gas cooler.
  • this includes Evaporator 10 between two end-side cover plates 11, 12 a stack of several flat tubes 1 according to FIGS. 1 and 2 with interposed, thermally conductive 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 clearly borrowed smaller than the flat tube width b.
  • a gap corresponding to the distance d between the two straight tube sections 2a, 2b of each flat tube 1 is formed between the two block parts.
  • the corrugated fins 8 extend in one piece over the entire flat tube depth and thus also over this gap, with them on both sides, i.e. can survive on the front and back of the block, as needed.
  • the block front is defined here by the fact that it is guided by a second temperature medium, e.g. Supply air to be cooled for a vehicle interior in which
  • Pipe transverse direction y i.e. in the depth direction of the block.
  • the transverse extension of the ends of the flat tube ends is less than the width of the flat tube b due to their twisting.
  • a common collecting pipe can be provided for both rows of stacks of pipe ends 6a, 6b, which is divided into the two required, separate collecting channels by means of a longitudinal partition.
  • the evaporator 10 with the tube / fin block 9 thus formed can be realized in a compact design and very pressure-stable and has a high heat transfer efficiency.
  • a heat transfer performance can be achieved with relatively narrow flat tubes, which would otherwise require at least approximately twice as wide, non-curved flat tubes.
  • the unique flat tube deflection means that the temperature control medium to be passed through the tube interior can be fed in and out on one and the same tube block side, which is advantageous in some applications.
  • 5 shows an embodiment in a serpentine construction.
  • 5 shows a plurality of serpentine flat tubes 13 which are stacked one above the other in any desired number to form the serpentine tube block there.
  • the serpentine flat tube 13 used for this is largely identical to that of FIGS. 1 and 2, with the exception that on both sides of the inverted bend section 3, which is similar to that of FIGS. 1 and 2, not only a straight, single-layer pipe section, but a multiple Connects serpentine coiled pipe section 12, which in turn face each other offset in the block depth direction by a corresponding gap.
  • the serpentine turns . 12 of the respective pipe coil section 13 are, as usual, by bending the flat pipe at the relevant point about the transverse pipe axis there by an angle of
  • heat-conductive corrugated fins 8 are introduced continuously from the front of the block to the rear of the block with an optional overhang. It goes without saying that here, as in the example of FIGS. 4 and 5, a corrugated fin row can be provided instead for each of the two rows of pipe blocks offset in the block depth, in which case the gap between the two rows of blocks can also remain free.
  • any other number of corrugated fins and / or corrugated fins with different widths can of course be used in each corrugated fin layer across the pipe block depth, for example a first one that extends over two thirds of the pipe block depth and a second one Corrugated fin extending over the remaining third of the tube block depth.
  • the gap favors the condensate separation of the evaporator.
  • the height of the heat-conducting fins 8 and thus the stacking distance between adjacent, straight flat tube sections both within a serpentine flat tube 13 and between two adjacent serpentine flat tubes 13 roughly corresponds to that opposite the Flat tube width b significantly lower height c of the reversing bend section 3 '.
  • the twisting chosen in this case of the flat tube ends 6, which in turn opens on the same block side, of 90 ° does not collide with this low stacking height, since the serpentine flat tubes 13 each have a greater height in the stacking direction z than the flat tube width 12 due to their flat tube sections.
  • the right-angled twisting of the ends 6 by 90 ° enables, as mentioned, the use of particularly narrow manifolds or manifolds forming them.
  • 5 shows such a collecting tube 7 on the front side, into which the front row of flat tube ends 6 opens.
  • the serpentine flat tubes 13 can be connected to the
  • Flat tube 1 of FIGS. 1 and 2 can be combined. Numerous other alternatives to the two flat tube designs shown are possible.
  • the flat tube can thus have two or more reversing bend sections and corresponding deflections.
  • serpentine flat tube 13 of FIG. 5 can be modified such that at least one further serpentine turn in one and / or in the other serpentine tube section causes the relevant flat tube end 6 to lie on the block side opposite the reversing bend section 3.
  • a serpentine flat tube 13 of the type shown in FIG. 5, but with one or more additional reversing bend sections 3, can be provided in order to build up a tube block for a serpentine heat exchanger that is at least three parts in the block depth direction.
  • the flat tube ends 6 can also be left undetected.
  • a two-chamber header tube can be used, which already has two separate, longitudinal tubes in the production stage Has hollow chambers. It is made from an extruded profile and integrally contains two separate longitudinal chambers, which form the collecting channels for the heat exchanger in question.
  • suitable circumferential slots are to be made in the manifold 7, into which the flat tube ends 6 are tightly inserted.
  • header pipes can also be used which, by means of appropriate transverse walls, contain several header channels separated from each other in the block vertical direction z.
  • This will the flat tubes in the tube block are combined into several groups in such a way that the tubes of a group are flowed through in parallel and the various tube groups are flowed through in series.
  • a supplied temperature control medium flows from a collection channel on the intake side into the group of flat tubes opening there and then arrives at the other end thereof in a collection channel functioning as a deflection chamber, into which a second group of flat tubes opens in addition to this first group, into which the temperature control medium is then deflected.
  • 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 manufactured with this are suitable e.g. also for comparatively high pressure CO2 air conditioning systems, such as are increasingly being considered for motor vehicles.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • External Artificial Organs (AREA)
  • Surgical Instruments (AREA)

Abstract

L'invention concerne un tube plat (1) présentant une section coudée en U (3), dans laquelle le tube plat (1) est coudé de telle manière que ses deux sections tubulaires planes (2a, 2b), adjacentes à la section coudée, s'étendent longitudinalement dans des sens d'écoulement opposés (4a, 4), les axes longitudinaux (5a, 5b) desdites sections planes étant décalés l'un par rapport à l'autre, au moins dans le sens transversal (y). Selon l'invention, la section coudée en U (3) est conçue de telle manière qu'un axe de coudage principal (A) est parallèle au plan du tube plat, et forme un angle prédéfini avec l'extension longitudinale des tubes, le plan du tube plat étant défini par l'extension en longueur et en largeur du tube plat (1).
PCT/EP2004/001257 2003-02-18 2004-02-11 Tube plat presentant une section coudee en u et echangeur thermique comportant un tel tube plat WO2004074756A2 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US10/545,889 US20060243432A1 (en) 2003-02-18 2004-02-11 Flat pipe comprising a return bend section and a heat exchanger constructed therewith
BRPI0407582-0A BRPI0407582A (pt) 2003-02-18 2004-02-11 tubo chato com seção da curva de retorno e com trocador de calor montado com ele
EP04710027A EP1597529B1 (fr) 2003-02-18 2004-02-11 Tube plat presentant une section coudee en u et echangeur thermique comportant un tel tube plat
DE502004004288T DE502004004288D1 (de) 2003-02-18 2004-02-11 Flachrohr mit umkehrbogenabschnitt und damit aufgebauter w r me bertrager
JP2006501805A JP2006518029A (ja) 2003-02-18 2004-02-11 反転アーチ部分を有するフラット管およびそれによって構築された熱伝達体

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10306848A DE10306848A1 (de) 2003-02-18 2003-02-18 Flachrohr mit Umkehrbogenabschnitt und damit aufgebauter Wärmeübertrager
DE10306848.1 2003-02-18

Publications (2)

Publication Number Publication Date
WO2004074756A2 true WO2004074756A2 (fr) 2004-09-02
WO2004074756A3 WO2004074756A3 (fr) 2004-10-21

Family

ID=32747996

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/001257 WO2004074756A2 (fr) 2003-02-18 2004-02-11 Tube plat presentant une section coudee en u et echangeur thermique comportant un tel tube plat

Country Status (8)

Country Link
US (1) US20060243432A1 (fr)
EP (1) EP1597529B1 (fr)
JP (1) JP2006518029A (fr)
CN (1) CN100362303C (fr)
AT (1) ATE366905T1 (fr)
BR (1) BRPI0407582A (fr)
DE (2) DE10306848A1 (fr)
WO (1) WO2004074756A2 (fr)

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Publication number Priority date Publication date Assignee Title
US10317141B2 (en) 2014-11-25 2019-06-11 Hydro Extruded Solutions As Multi port extrusion tubing design

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DE102006018688B4 (de) * 2006-04-13 2009-08-27 Visteon Global Technologies Inc., Van Buren Verfahren zum Biegen von Multiportrohren für Wärmeübertrager
US20080302518A1 (en) * 2007-06-07 2008-12-11 Joseph Durdel Flat tube heat exchanger
WO2010072221A2 (fr) * 2008-12-23 2010-07-01 Noise Limit Aps Dispositif de refroidissement comprenant un tuyau plat courbé et procédé de fabrication associé
PL2218978T3 (pl) * 2009-02-17 2011-09-30 Cockerill Maintenance & Ingenierie Wymiennik ciepła typu flagi
CN101850391B (zh) * 2009-03-31 2012-07-04 三花丹佛斯（杭州）微通道换热器有限公司 扁管加工方法及扁管、热交换器加工方法及热交换器
DE102009047620C5 (de) * 2009-12-08 2023-01-19 Hanon Systems Wärmeübertrager mit Rohrbündel
CN101846465B (zh) * 2010-04-13 2011-11-09 三花丹佛斯（杭州）微通道换热器有限公司 换热器
CN101936672B (zh) * 2010-09-15 2012-09-19 三花控股集团有限公司 具有改善的表面空气流场分布均匀性的换热器
CN201945091U (zh) * 2010-11-18 2011-08-24 三花丹佛斯（杭州）微通道换热器有限公司 一种换热器
CN103644685A (zh) * 2013-12-26 2014-03-19 杭州三花微通道换热器有限公司 换热器和具有该换热器的多制冷系统空调
US20160363387A1 (en) * 2015-06-12 2016-12-15 Hamilton Sundstrand Space Systems International, Inc. Phase-change material heat exchanger
CN113654394A (zh) * 2021-08-05 2021-11-16 浙江酷灵信息技术有限公司 换热器

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EP0659500A1 (fr) 1993-12-20 1995-06-28 MAGNETI MARELLI CLIMATIZZAZIONE S.r.l. Procédé de pliage d'un tube de section oblongué et échangeur de chaleur à tubes de section oblongué et plié en forme de U
DE19830863A1 (de) 1998-07-10 2000-01-13 Behr Gmbh & Co Flachrohr mit Querversatz-Umkehrbogenabschnitt und damit aufgebauter Wärmeübertrager

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JP3043051B2 (ja) * 1990-11-22 2000-05-22 昭和アルミニウム株式会社 熱交換装置
JP3305460B2 (ja) * 1993-11-24 2002-07-22 昭和電工株式会社 熱交換器
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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Publication number Priority date Publication date Assignee Title
EP0659500A1 (fr) 1993-12-20 1995-06-28 MAGNETI MARELLI CLIMATIZZAZIONE S.r.l. Procédé de pliage d'un tube de section oblongué et échangeur de chaleur à tubes de section oblongué et plié en forme de U
DE19830863A1 (de) 1998-07-10 2000-01-13 Behr Gmbh & Co Flachrohr mit Querversatz-Umkehrbogenabschnitt und damit aufgebauter Wärmeübertrager

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10317141B2 (en) 2014-11-25 2019-06-11 Hydro Extruded Solutions As Multi port extrusion tubing design

Also Published As

Publication number Publication date
WO2004074756A3 (fr) 2004-10-21
EP1597529A2 (fr) 2005-11-23
DE502004004288D1 (de) 2007-08-23
CN100362303C (zh) 2008-01-16
DE10306848A1 (de) 2004-08-26
BRPI0407582A (pt) 2006-02-14
EP1597529B1 (fr) 2007-07-11
CN1751216A (zh) 2006-03-22
ATE366905T1 (de) 2007-08-15
US20060243432A1 (en) 2006-11-02
JP2006518029A (ja) 2006-08-03

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