EP1597529B1 - 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

Info

Publication number
EP1597529B1
EP1597529B1 EP04710027A EP04710027A EP1597529B1 EP 1597529 B1 EP1597529 B1 EP 1597529B1 EP 04710027 A EP04710027 A EP 04710027A EP 04710027 A EP04710027 A EP 04710027A EP 1597529 B1 EP1597529 B1 EP 1597529B1
Authority
EP
European Patent Office
Prior art keywords
flat
heat exchanger
flat pipe
pipe
tube
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
EP04710027A
Other languages
German (de)
English (en)
Other versions
EP1597529A2 (fr
Inventor
Walter Demuth
Wolfgang Geiger
Martin Kotsch
Michael Kranich
Karl-Heinz Staffa
Christoph Walter
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 EP1597529A2 publication Critical patent/EP1597529A2/fr
Application granted granted Critical
Publication of EP1597529B1 publication Critical patent/EP1597529B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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 heat exchanger according to the preamble of claim 1.
  • a flat tube of a generic heat exchanger with a reverse arc section and such a heat exchanger with a built-up of this flat tube tube block are in the published patent application DE 198 30 863 A1 described.
  • the flat tube is bent in such a way that its two adjoining, planar tube sections extend in the longitudinal direction with opposite throughflow directions and with longitudinal axes offset at least in the transverse direction.
  • the publication EP 0 659 500 A1 also describes a flat tube with reverse arc section and a heat exchanger with a constructed from this flat tube type pipe block.
  • a rectilinear flat-tube blank is first bent out of the flat tube plane in a U-shape until the flat-tube limbs run parallel to one another, after which the latter are twisted by 90 [deg.] Relative to the U-arc region.
  • the resulting flat tube has thus two lying in a plane, planar pipe sections whose mouth ends lie on the same, the reverse arc section opposite side.
  • the JP-4-187990 discloses a heat exchanger in which the tubes are angled in the middle.
  • the object of the invention is to provide a flat tube with a Um Spotifybogenabites, which can be relatively easily produced and is suitable for building very pressure-stable heat exchanger with little space, and to provide a constructed of such flat tubes heat exchanger.
  • the main idea of the invention is to form an inverted arc section such that a main bending axis parallel to the Flat tube level and extends at a predetermined angle to Rohrlijnserstrekkung, the flat tube level is determined by the length and width of the flat tube.
  • the predefinable angle is 90 °, ie the main bending axis then runs perpendicular to the tube longitudinal extent.
  • the flat tube according to the invention is displaced parallel to the tube extension by a distance s during the forming in the region of the reversal arc section in the flat tube plane, wherein the path s is 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 merge into the reverse curve section is freely selectable during the deformation 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 runs perpendicular to the flat tube plane.
  • the displacement of the flat tube is achieved by two bending operations around two bending axes, which are performed before or after the main bending process about the first bending axis, wherein the first bending axis extends in the middle of the offset region, wherein the offset region approximately twice as long as the reverse arc section.
  • the two planar tube sections adjoining the reverse curve section are arranged lying perpendicularly to the stacking direction z after the forming process in mutually laterally offset parallel planes, preferably with a spacing d in the transverse direction y between 0.2 mm and 20 mm.
  • the tube block depth per reversal arc section increases by the flat tube width plus the said transverse spacing d of the planar tube sections. Due to the transverse spacing, corresponding gaps are formed between the flat tube sections in a tube block constructed with such flat tubes, which facilitates the separation of condensed water, e.g. in the application of the tube block in an evaporator of a motor vehicle air conditioner.
  • the reverse arc section is reshaped such that the two tube sections lie next to one another and parallel to the distance d in a common plane. This can be done by a symmetrical or asymmetrical deformation of the reverse arc section.
  • a serpentine tube block can be realized, the depth of which depends on the number of first reverse arc sections formed one behind the other.
  • first and second Umlopebogenabitesen in which the direction of the offset is also carried out opposite, can be, for example, a tube block serpentine construction with a depth of double the flat tube width plus the said distance d between the planar pipe sections realize in which a Temperiermedium, for example, a refrigerant or a coolant, first flows through the flat pipe sections, which lie in a common plane, and then flows through the flat pipe sections, which lie in the stacking direction or against the stacking direction in the next common plane.
  • a Temperiermedium for example, a refrigerant or a coolant
  • third reverse bend section - for example in the stacking direction and subsequently a first reverse bend section is formed which has a number of second reverse bend sections connect.
  • a second reverse bend section can also be arranged instead of the first reverse bend section.
  • the main bending process is performed around the main bending axis at a predetermined angle to the pipe extension, wherein the predetermined angle substantially corresponds to the angle ⁇ , with which the flat pipe sections pass into the reverse bend portion.
  • the two flat tube sections lie in two mutually parallel planes, wherein the two flat tube sections enclose an angle with a value of 2 ⁇ .
  • the two pipe legs are each transformed with a further bending operation about a bending axis which is perpendicular to the flat tube plane, so that they each transition at the angle ⁇ in the Umledgebogenabites.
  • the procedure described provides in another way the required offset of the flat tube already described.
  • the reverse arc section can be realized by relatively simple tube bending operations.
  • the flat tube can be bent once or several times in this way, with its depth dimension, i. its extension in the transverse direction as defined above increases with each bend when the lateral offset always occurs in the same direction.
  • transverse or depth direction usually represents that direction in which a medium to be cooled or heated is passed through outside of the flat tube surfaces by the heat exchanger.
  • additional heat-conducting fins are usually provided between the stacked pipe block sections in order to improve the heat transfer. Since, as I said, the pipe interspaces can be kept very tight, also correspondingly low heat-conducting corrugated fins can be used, which also improves the compactness and stability of a tube-finned block thus formed.
  • a plurality of flat tubes according to the invention are stacked in the stacking direction z to form a tube block.
  • the flat tubes open with one end in at least one laterally arranged in the stacking direction of the tube block collecting channel, wherein at least one of the two, via the reverse arc section interconnected pipe sections can form a serpentine winding 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 inventive design of the flat tubes with a 180 ° deflection in the flow direction it is possible to realize a smaller space for the heat exchanger such as a gas cooler or an evaporator, since tighter distances in the stacking direction and / or between the tubes can be realized.
  • a springing of the flat tube legs is almost avoided.
  • the heat exchangers constructed with the flat tubes according to the invention have a stiffer construction with narrower tolerances.
  • the refrigerant is conducted in a flat tube in a cross-countercurrent to the air.
  • the flat tube runs in the same plane as on the way back, but laterally offset by a distance s, so that the leading portion of the flat tube is spaced from the returning section by a distance d.
  • the two flat pipe sections lie in the same plane, which is determined by the longitudinal and width extension of the flat tubes in their straight sections.
  • the transformation is preferably carried out in three stages. In the first stage, the flat tube experiences a lateral offset from the extended state. The amount of offset s corresponds to the sum of flat tube width b and distance d.
  • a bend is made with a radius r about 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 is approximately in the middle of the offset range.
  • the sections of the flat tube are then parallel to each other in different levels.
  • the reverse bend section is reshaped, that the flat pipe sections are again in a common plane.
  • the deformed reverse bend portion may 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 reverse bend section to the common plane are possible.
  • the transformation steps can also be reversed.
  • the flat tube according to the invention forms a serpentine flat tube by at least one of the two connected via a reverse arc section flat tube sections is bent in the stacking direction to a Rohrserpentine, ie it consists of stacking direction successive third Umledgebogenabroughen with the corresponding planar pipe sections.
  • the mouth ends lie on the same or on opposite sides, wherein at least one end, preferably both ends, are twisted in relation to the adjoining center region.
  • 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 construction.
  • the heat exchanger is both in single-layer construction, in which the flat pipe sections between two Umscenebogenabêten or between a Umnovabogenabterrorism and a flat pipe end of a flat, straight pipe section, as well as Serpentine in executable, in which these flat pipe sections are bent into a coil.
  • the collecting ducts can then be formed by a respective collecting tank or collector pipe, which run along the respective pipe block side along the stacking direction, also referred to as Blockrochraum and serve the parallel supply or discharge of the guided through the pipe interior tempering to or from the individual flat tubes.
  • the flat tube ends all open on the same tube block side. Due to the design of the flat tubes while the two tube ends of each flat tube are offset from each other in the block depth direction, so that they can be assigned to two corresponding in the block depth direction adjacent collecting channels. Accordingly, supply and discharge of the tempering medium conducted through the tube interior takes place on the same heat exchanger side.
  • this type of heat exchanger with two adjacent collecting ducts on the same side of the tube block is provided to form these collecting ducts by two separate manifolds or manifolds, hereinafter referred to simply as collectors for the sake of simplicity, or to form a common manifold.
  • collectors for the sake of simplicity
  • the latter can be realized that an initially uniform collecting tube interior is divided with a longitudinal partition in the two collecting channels, or in that the manifold is made as an extruded tube profile with two separate, the collecting channels forming hollow chambers.
  • At least one of the two manifolds or at least one of the two hollow chambers of a longitudinally divided manifold divided by transverse partitions in several, in block vertical direction separate collection channels.
  • a groupwise serial flow through the flat tubes in the tube block is achieved by first feeding the tube block via a first collection channel of the transversely divided collection tube or the transverse split chamber supplied temperature control only in the there opening part of all flat tubes.
  • the collection channel, in which this part of the flat tubes opens with the other end of the tube then acts as a deflection channel, in which the temperature control medium is deflected by the flat tubes opening out there into a further part of all the flat tubes which also opens there with one end.
  • Number and position of the transverse partitions determine the division of the flat tubes in successively flowed through groups of parallel flowed flat tubes.
  • a flat tube produced according to the invention the arrangement of the flat tubes with respect to a flow of air remains unchanged despite the reversal arc section, d. H. one of the air-facing side of the flat tube is still after the reverse arc portion of the air and faces away from the air side of the flat tube is still facing away from the air even after the reverse arc section.
  • the flat tube 1 shown in a plan view in FIG. 1 is manufactured in one piece from a rectilinear multi-chamber profile using suitable bending processes. It comprises two planar, rectilinear pipe sections 2a, 2b, which are connected to one another via an inverted arc section 3 and have opposite directions of flow for a tempering medium passed through the plurality of parallel chambers in the interior of the flat tube 1, for example a coolant of a motor vehicle air conditioning system.
  • a tempering medium passed through the plurality of parallel chambers in the interior of the flat tube 1, for example a coolant of a motor vehicle air conditioning system.
  • One of the two possible flow paths is shown in FIG. 1 by corresponding flow arrows 4a, 4b.
  • the parallel to the flow directions 4a, 4b extending longitudinal axes 5a, 5b of the two plan, rectilinear pipe sections 2a, 2b define a longitudinal direction x and are offset from each other in a transverse direction y perpendicular thereto.
  • the two planar pipe sections 2 a, 2 b are arranged with a first reverse bend section 3 in a common xy plane, which is perpendicular to a stacking direction z, in which a plurality of such flat pipes form a Heat exchanger tube block are stacked, as will be explained in more detail below with reference to FIGS. 4 and 5.
  • the respective coordinate axes x, y, z are shown in FIGS. 1 to 5.
  • the reverse curve section 3 is obtained by the fact that the initial, straight flat tube profile of a desired width b in the region of an offset region U as shown in Fig. 3a is displaced in the flat tube plane parallel to the tube extension by a distance s, resulting from the tube width b and the desired Distance d 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 pipe sections 2 a, 2 b and the reverse bend section 3 takes place at a predeterminable angle ⁇ .
  • the angle ⁇ and / or the path s are achieved by at least one bending operation about at least one bending axis B1, B2, which runs perpendicular to the flat tube plane.
  • the described offset is achieved by the path s by two bending operations about the bending axes B1 and B2 shown in Fig. 3a, these two bending operations preferably being performed around the main bending axis A before the bending operation.
  • the main bending axis A runs in the illustrated embodiment in the middle of the offset region U, the offset region U being approximately twice as long as the reverse bend segment 3.
  • the two straight pipe sections 2a, 2b of the flat tube 1 are the two rectilinear pipe sections 2a, 2b as shown in Fig. 2a offset in mutually parallel planes with a selectable distance 2r in the z direction and in the selectable distance d in the y direction, wherein for the maximum inner radius r: ( h r -d FR ) / 2, where h r is the fin height and d FR is the flat tube thickness, this results in a reasonable lower limit for r the flat tube thickness d FR .
  • a reasonable value for the angle ⁇ lies in the limits 13 ° ⁇ ⁇ 67 °.
  • the selectable distance 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 rectilinear pipe sections 2a, 2b are connected on the one side via the reverse bend section 3, they both extend 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 longitudinal axis parallel thereto, i. with a transverse offset with respect to the longitudinal central axis, by any angle between 0 ° and 90 °, wherein in the case shown, the torsion angle is about 90 °.
  • FIG. 2 it is clear that due to the described formation of the reverse arc portion 3, the height c of the reverse arc portion 3 and thus the expansion in the stacking direction z is small and depending on the bending radius is selectable. In particular, this height c of the reverse bend section 3 remains significantly smaller than the flat tube width b. As a result, a plurality of such flat tubes can be stacked in a heat exchanger tube block with a stack height, which 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 that the two planar pipe sections 2a, 2b as shown in Fig. 2a are in two staggered xy planes. In this case, the transverse direction y is defined by the fact that they are both for Longitudinal x of the straight pipe sections and the pipe block stacking direction z is perpendicular.
  • Fig. 3b shows an alternative possibility for the design of the reverse bend portion 3 after a main bending operation.
  • the main bending process is performed around the bending axis A only before the offset is realized by further bending operations about a bending axis B3.
  • the main bending axis A extends at the predeterminable angle ⁇ in the limits of 13 ° ⁇ ⁇ 67 ° to the tube longitudinal extension.
  • the two pipe sections are bent in each case around the bending axis 3 according to the arrows inwards. According to the illustration in FIG.
  • the distance d between the flat tubes is realized by a limitation, realized in the illustrated example by a delimiting strip with the width d, wherein in the illustrated example the bending axis B3 is realized by an upper end of the delimiting strip.
  • the illustrated flat tube sections 2a and 2b lie in different parallel planes and include a diaper of 2 ⁇ . After the additional bending operations, the two flat pipe sections 2a and 2b are parallel to each other in the different parallel planes, as shown in Fig. 2a, so that the other already described forming steps can be performed to achieve that the two flat pipe sections 2a, 2b in parallel with the distance d lie in a common plane (see Fig. 2b to 2c).
  • FIG. 4 and 5 show an application for the flat tube type of Fig. 1 and 2 in the form of a tube / rib block 9 of an evaporator 10, as it is particularly useful in automotive air conditioning systems.
  • the heat exchanger shown in some sections can also be used for any other heat transfer purposes, for example as a gas cooler, depending on the design.
  • this includes Evaporator 10 between two end cover plates 11, 12 a stack of several flat tubes 1 of FIG. 1 and 2 with intermediate, thermally conductive corrugated fins 8.
  • the height of the heat-conducting ribs 8 corresponds approximately to the height c of the flat-tube reverse arc sections 3 and is thus significantly smaller than the flat tube width b.
  • a tube-fin block 9 having in depth, i. formed in the y-direction, two-part structure, wherein in each of the two block parts in each case the pipe sections with the same flow direction in the stacking direction z are superimposed. Between the two block parts a distance d of the two straight tube sections 2a, 2b of each flat tube 1 corresponding gap is formed.
  • the corrugated fins 8 extend in the illustrated embodiment in one piece over the entire flat tube depth and thus also across this gap, where they are on both sides, i. At the front and at the back of the block, can survive as needed. But it is also possible to use multi-part, in particular two-part corrugated fins 8.
  • the block front side is in this case defined by the fact that it is from a second tempering medium routed on the outside over the evaporator surfaces, e.g. supply air to be cooled for a vehicle interior, in the tube transverse direction y, i. in the block depth direction, is flown.
  • a second tempering medium routed on the outside over the evaporator surfaces, e.g. supply air to be cooled for a vehicle interior, in the tube transverse direction y, i. in the block depth direction, is flown.
  • the transverse extent of the flat tube mouth ends is smaller than the flat tube width b due to their twisting.
  • the flat tube ends of about 90 ° even only needs to be slightly larger than the flat tube thickness. It is therefore easily possible, two manifolds on the relevant side of the tube block side by side in the stacking direction z running to arrange to receive each one of the two ends of each flat tube 1.
  • a common manifold for both rows of stacking pipe ends 6a, 6b may be provided, which is divided by a longitudinal partition in the two required, separate collection channels.
  • the evaporator 10 can be realized with the thus formed tube / rib block 9 in a compact design and very pressure stable and thereby has a high heat transfer efficiency.
  • By bending the flat tubes to two offset in the block depth pipe sections 2a, 2b can be achieved with relatively narrow flat tubes heat transfer performance for the otherwise at least about twice as wide, not bent flat tubes would be required.
  • At the same time is achieved by the one-time Flachrohrumlenkung that the passing through the inside of the tube temperature control on one and the same side of the tube block can be supplied and removed, which is advantageous in some applications.
  • FIG. 5 an embodiment is shown in 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 local serpentine tube block.
  • the serpentine flat tube 13 used for this purpose is largely identical to that of FIGS. 1 and 2, with the exception that on both sides of the same to that of FIGS. 1 and 2 reverse arc section 3 not only a straight, single-layer pipe section, but a multiple serpentine wound tube coil section 12 connects, which in turn are offset in block depth direction by a corresponding gap.
  • the serpentine turns 12 of the respective tube coil section 13 are formed as usual by bending the flat tube at the relevant point about the local pipe transverse axis by an angle of 180 °.
  • each corrugated fin row for each of the two offset in the block depth direction tube block rows, in which case, the gap between the two rows of blocks can remain free.
  • any other number of corrugated fins and / or corrugated fins having different widths can be inserted across the tube block depth, eg a first, extending over two thirds of the tube block depth and a second, over the remaining third of the tube block depth extending corrugated fin.
  • the gap promotes the condensation of the evaporator.
  • the height of the heat-conducting ribs 8 and thus the stack spacing of adjacent straight-line flat pipe sections also corresponds within a serpentine flat tube 13 and between two adjacent serpentine flat tubes 13 approximately in relation to FIG Flat tube width b significantly lower height c of the reverse arc section 3 '.
  • the twisting of the flat tube ends 6 of 90 ° which in turn opens on the same block side, does not collide with this small stack height, since the serpentine flat tubes 13, due to their tube coil sections 12, each have a greater height than the flat tube width in the stacking direction z.
  • the orthogonal twisting of the ends 6 by 90 ° allows, as mentioned, the use of particularly narrow collecting ducts or these forming headers.
  • a front-side manifold 7 is shown, in which the front row of the flat tube ends 6 opens.
  • the serpentine flat tubes 13 with the flat tube 1 of Figs. 1 and 2 are combined.
  • the flat tube may have two or more reverse arc sections and corresponding deflections.
  • serpentine flat tube 13 of FIG. 5 can be modified such that the respective flat tube end 6 comes to rest on at least one further serpentine turn in one and / or in the other serpentine tube section on the block side opposite the reverse bend section 3.
  • a serpentine flat tube 13 of the type shown in FIG. 5, but with one or more additional reverse bend sections 3, can be provided so as to build up a block block at least three-part tube block for a serpentine heat exchanger.
  • the flat tube ends 6 can also be left untraded.
  • a two-chamber manifold can be used, which already in the manufacturing stage two separate, longitudinal Has hollow chambers. It is made of an extruded profile and integrally includes two separate longitudinal chambers, which form the collecting channels for the relevant heat exchanger. For this purpose, as in the other Samelrohraus exchangeen, introduce appropriate peripheral slots in the manifold 7, in which the flat tube ends 6 are tightly inserted.
  • manifolds which contain a plurality of collecting ducts which are separated from one another in the block vertical direction z by means of corresponding transverse walls.
  • This will be the flat tubes in the tube block to several groups summarized such that the tubes of a group in parallel and the various tube groups are flowed through serially.
  • a supplied tempering medium flows from an inlet-side collecting channel into the group of flat tubes which open out there and then arrives at the other end in a collecting channel functioning as a deflection space, into which a second flat tube group opens adjacent to this first group, into which the temperature control medium is then deflected.
  • This can be continued by appropriate positioning of the transverse walls in one or both headers in any way up to an exit-side collecting duct, via which the tempering then leaves the tube block.

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)
  • Surgical Instruments (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • External Artificial Organs (AREA)

Claims (14)

  1. Echangeur de chaleur à tube plat pour une installation de climatisation de véhicule automobile, comprenant un bloc tubulaire (9) avec un ou plusieurs tubes plats (1) empilés les uns au-dessus des autres dans un sens d'empilement (z), des conduits collecteurs (7) agencés le long du sens d'empilement (z) étant disposés sur le côté du bloc tubulaire (9), conduits dans lesquels les tubes plats (1) débouchent chacun par une extrémité (6), le tube plat étant doté d'une partie de coude en U, dans laquelle le tube plat (1) est replié de telle sorte que ses deux parties de tube (2a, 2b) planes s'y raccordant sont agencées parallèlement entre elles dans le sens longitudinal avec des directions d'écoulement (4a, 4b) opposées et se situent dans le même plan ou dans des plans x-y décalés en parallèle, caractérisé en ce que la partie de coude en U (3) est obtenue par le fait que le profil de tube plat rectiligne initial de largeur b est décalé d'une course s dans le secteur d'une zone de déport U dans le plan du tube plat parallèlement à l'extension du tube, laquelle course se compose de la largeur du tube b et d'une distance d souhaitée entre les parties du tube plat (2a, 2b) après la déformation, la transition entre les parties de tube plat (2a, 2b) et la partie de coude en U (3) s'effectuant avec un angle (α) prédéfinissable.
  2. Echangeur de chaleur à tube plat selon la revendication 1, caractérisé également en ce que l'angle prédéfinissable est de 90°.
  3. Echangeur de chaleur à tube plat selon l'une quelconque des revendications 1 ou 2, caractérisé en ce que l'angle (α) et/ou la course (s) est obtenu par au moins une opération de pliage autour d'au moins un axe de pliage (B), qui est perpendiculaire au plan du tube plat.
  4. Echangeur de chaleur à tube plat selon la revendication 3, caractérisé également en ce que le déplacement du tube plat (1) est obtenu par deux opérations de pliage autour de deux axes de pliage (B1, B2), qui sont effectuées avant ou après l'opération de pliage principale autour du premier axe de pliage (A), le premier axe de pliage (A) passant au centre d'une zone de déport (U).
  5. Echangeur de chaleur à tube plat selon l'une quelconque des revendications précédentes, caractérisé également en ce que les deux parties de tube (2a, 2b) planes, se raccordant à la partie de coude en U (3) sont disposées dans des plans parallèles entre eux perpendiculairement à la direction d'empilement (z) à une distance (d).
  6. Echangeur de chaleur à tube plat selon l'une quelconque des revendications précédentes, caractérisé également en ce que, dans une autre opération de déformation, la partie de coude en U (3) est déformée de telle sorte que les deux branches de tube (2a, 2b) sont disposées l'une à côté de l'autre et en parallèle à la distance (d) dans un même plan.
  7. Echangeur de chaleur à tube plat selon l'une quelconque des revendications précédentes, caractérisé également en ce que la partie de coude en U (3) est déformée de façon symétrique ou asymétrique.
  8. Echangeur de chaleur à tube plat selon l'une quelconque des revendications précédentes, caractérisé en ce que la distance (d) dans la direction transversale (y) est comprise entre 0,2 mm et 20 mm.
  9. Echangeur de chaleur à tube plat selon l'une quelconque des revendications précédentes, caractérisé en ce que, par la partie de coude en U (3), un côté, tourné vers l'air de la partie de tube plat (2a) devient un côté tourné vers l'air de la partie de tube plat (2b) et un côté, opposé à l'air, de la partie de tube plat (2a) devient un côté, opposé à l'air, de la partie de tube plat (2b).
  10. Echangeur de chaleur à tube plat selon l'une quelconque des revendications précédentes, caractérisé en ce que, par la partie de coude en U (3), un côté inférieur de la partie de tube (2a) devient le côté supérieur de la partie de tube (2b) et un côté supérieur de la partie de tube (2a) devient le côté inférieur de la partie de tube (2b).
  11. Echangeur de chaleur à tube plat selon l'une quelconque des revendications précédentes, caractérisé en ce que les deux extrémités de tube plat (6) sont situées sur les mêmes côtés ou sur des côtés opposés et au moins l'une des deux extrémités de tube (6a, 6b) est tordue d'un angle compris entre 0° et 90°.
  12. Echangeur de chaleur à tube plat selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins l'une des deux parties de tube (2a, 2b) reliées entre elles au moyen de la partie de coude en U (3) forme un serpentin tubulaire (12) tourné dans le sens d'empilement (z).
  13. Echangeur de chaleur à tube plat (6) selon au moins l'une quelconque des revendications précédentes 1 à 12, caractérisé en ce que l'échangeur de chaleur est un refroidisseur à gaz.
  14. Echangeur de chaleur à tube plat (10) selon au moins l'une quelconque des revendications précédentes 1 à 12, caractérisé en ce que l'échangeur de chaleur est un évaporateur.
EP04710027A 2003-02-18 2004-02-11 Tube plat presentant une section coudee en u et echangeur thermique comportant un tel tube plat Expired - Lifetime EP1597529B1 (fr)

Applications Claiming Priority (3)

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

Publications (2)

Publication Number Publication Date
EP1597529A2 EP1597529A2 (fr) 2005-11-23
EP1597529B1 true EP1597529B1 (fr) 2007-07-11

Family

ID=32747996

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04710027A Expired - Lifetime EP1597529B1 (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)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
ATE505693T1 (de) * 2009-02-17 2011-04-15 Cockerill Maintenance & Ingenierie Fahnenwärmetauscher
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
CN107000007B (zh) * 2014-11-25 2019-10-01 萨帕股份公司 多孔口挤压管设计
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

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2209325C3 (de) * 1970-05-18 1978-08-03 Noranda Metal Industries Inc., Bellingham, Wash. (V.St.A.) Wärmeaustauschrohr
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
IT1272091B (it) * 1993-12-20 1997-06-11 Borletti Climatizzazione Procedimento per la piegatura di un tubo a sezione trasversale oblunga e scambiatore di calore con tubi a sezione oblunga piegati a u
DE19830863A1 (de) * 1998-07-10 2000-01-13 Behr Gmbh & Co Flachrohr mit Querversatz-Umkehrbogenabschnitt und damit aufgebauter Wärmeübertrager
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

Also Published As

Publication number Publication date
US20060243432A1 (en) 2006-11-02
BRPI0407582A (pt) 2006-02-14
CN1751216A (zh) 2006-03-22
DE502004004288D1 (de) 2007-08-23
WO2004074756A2 (fr) 2004-09-02
EP1597529A2 (fr) 2005-11-23
CN100362303C (zh) 2008-01-16
WO2004074756A3 (fr) 2004-10-21
ATE366905T1 (de) 2007-08-15
JP2006518029A (ja) 2006-08-03
DE10306848A1 (de) 2004-08-26

Similar Documents

Publication Publication Date Title
EP1036296B1 (fr) Tube plat avec une partie coudee en u, decalee transversalement, et echangeur de chaleur con u a partir de ce dernier
EP2026028B1 (fr) Échangeur de chaleur, en particulier pour véhicule automobile
EP1042641B1 (fr) Bloc tubulaire d'echangeur thermique et tube plat multichambre utilisable a cet effet
DE60011616T2 (de) Wärmetauscher mit mehrkanalrohren
DE69911131T2 (de) Wärmetauscher
EP0845647B1 (fr) Echangeur de chaleur à tubes plats avec extrémité de tubes déformée par torsion
EP1597529B1 (fr) Tube plat presentant une section coudee en u et echangeur thermique comportant un tel tube plat
EP0401752A2 (fr) Condenseur de réfrigérant pour une installation de conditionnement d'air de véhicule
EP1701125A2 (fr) Echangeur de chaleur à tubes plats et tube plat pour échangeur de chaleur
DE112005001295T5 (de) Wärmetauscher
DE10257767A1 (de) Wärmeübertrager
EP1411310B1 (fr) Echangeur de chaleur à structure en serpentin
EP1203922A2 (fr) Condenseur et tube pour celui-ci
DE10150213A1 (de) Stranggepreßtes Profil, insbesondere für Wärmetauscher
EP1588115B1 (fr) Echangeur thermique, notamment refroidisseur de gaz
EP0845648B1 (fr) Echangeur de chaleur à tubes plats, en particulier condenseur de type à serpentin
EP1934545B1 (fr) Corps chauffant, circuit de refrigerant, appareil de climatisation pour une installation de climatisation de vehicule automobile, et installation de climatisation pour un vehicule automobile
EP2937658B1 (fr) Fluide caloporteur interne
DE102007001430A1 (de) Wärmetauscher
EP1321734A1 (fr) Echangeur de chaleur à tubes plats et procédé de fabrication
EP1166025B1 (fr) Echangeur thermique multibloc
EP2049859B1 (fr) Climatisation pour véhicule à moteur
EP1248063B1 (fr) Echangeur de chaleur
EP1293743B1 (fr) Bloc de tubes plats avec extrémités déformées pour échangeur de chaleur
DE102020213172A1 (de) Stapelscheibe für einen Stapelscheibenwärmeübertrager und zugehöriger Stapelscheibenwärmeübertrager

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050919

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: BEHR GMBH & CO. KG

RIN1 Information on inventor provided before grant (corrected)

Inventor name: WALTER, CHRISTOPH

Inventor name: KOTSCH, MARTIN

Inventor name: GEIGER, WOLFGANG

Inventor name: DEMUTH, WALTER

Inventor name: KRANICH, MICHAEL

Inventor name: STAFFA, KARL-HEINZ

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 502004004288

Country of ref document: DE

Date of ref document: 20070823

Kind code of ref document: P

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20071011

ET Fr: translation filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071022

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071011

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071211

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071012

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20080219

Year of fee payment: 5

26N No opposition filed

Effective date: 20080414

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071011

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20080215

Year of fee payment: 5

BERE Be: lapsed

Owner name: BEHR G.M.B.H. & CO. KG

Effective date: 20080228

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080229

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080228

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20090211

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20091030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090302

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080211

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080112

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070711

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080229

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20110315

Year of fee payment: 8

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004004288

Country of ref document: DE

Effective date: 20120901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120901