EP1036296A1 - Flachrohr mit querversatz-umkehrbogenabschnitt und damit aufgebauter wärmeübertrager - Google Patents
Flachrohr mit querversatz-umkehrbogenabschnitt und damit aufgebauter wärmeübertragerInfo
- Publication number
- EP1036296A1 EP1036296A1 EP99945947A EP99945947A EP1036296A1 EP 1036296 A1 EP1036296 A1 EP 1036296A1 EP 99945947 A EP99945947 A EP 99945947A EP 99945947 A EP99945947 A EP 99945947A EP 1036296 A1 EP1036296 A1 EP 1036296A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tube
- flat
- flat tube
- block
- heat exchanger
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
- F28D1/0478—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0475—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
- F28D1/0476—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
- F28D2021/0085—Evaporators
Definitions
- the invention relates to a flat tube according to the preamble of claim 1 and to a flat tube heat exchanger according to the preamble of claim 5.
- a flat tube and a heat exchanger with a tube block of this type constructed from this type of flat tube are described in the published patent application EP 0 659 500 AI.
- 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 twisted by 90 ° relative to the U-bend region.
- the resulting flat tube thus has two planar tube sections lying in one plane, the ends of which end on the same side opposite the primary bend section.
- the angle which the flat tube transverse axis encloses along the reversing bend section with the plane in which the rectilinear pipe legs lie initially increases over one torsion range from zero to the value of 90 ° at the head end of the reversing bend section, and then over the other torsion range to decrease again to 0 °.
- the expansion of the flat tube is therefore perpendicular to the plane the / plan pipe leg in the head area of the reverse bend section of the flat pipe width.
- the heat exchanger tube block there, several such flat tubes are stacked one above the other in the direction perpendicular to the plane of the straight flat tube legs, the stacking distance between the straight tube legs of adjacent flat tubes being greater than the flat tube width due to the expansion of the reversing arc sections in this direction corresponding to the width of the flat tubes must be kept.
- the flat tubes of the tube block which are designed in a single chamber, open into a collector arranged on one side of the tube block, which is divided by a longitudinal partition into two collecting spaces, into which the flat tubes each end with one end or the other.
- a heat exchanger with a tube block which is formed from a stack of round tubes which are U-shaped using a single reversing arc section or using a plurality of successive reversing arc sections as a pipe coil, the tube sections between the Reverse arc sections are straight and flattened.
- the flattened pipe sections of the round pipe lie offset in one plane, while the reversing bend section (s) and the two pipe end areas opening on the same side maintain the circular pipe cross section.
- the straight pipe sections are flattened using flat presses.
- the round ends of the pipes open into a collection or distribution space, that of a collection and distribution pipe or of a longitudinally divided one. Collection and distribution box are formed.
- the distance between the flattened pipe sections of adjacent pipes in the pipe block stack must necessarily be larger than the diameter of the round pipes used.
- US Pat. No. 3,416,600 discloses a heat exchanger in a serpentine construction, which has a tube fin block O 00/03190
- each serpentine flat tube is twisted by 90 °, and the two header tubes have corresponding, spaced-apart through-slots in which the twisted tube ends are received in a fluid-tight manner.
- each serpentine flat tube is twisted by 180 ° in a lateral block area in the vicinity of a serpentine turn, so that each flow channel of the multi-chamber flat tubes used faces part of a block front side and part of the opposite block rear side.
- a heat exchanger with a tube / fin block which contains a stack of straight multi-chamber flat tubes which are twisted at their two opposite ends by an angle of at most 45 ° and open into associated header tubes which are provided on their circumference with corresponding oblique slots which are spaced apart in the longitudinal direction of the collecting tube.
- the invention is based on the technical problem of providing a flat tube of the type mentioned at the outset, which can be produced relatively easily and is suitable for building very pressure-stable heat exchangers with a small internal volume and high heat transfer efficiency, and a heat exchanger constructed from such flat tubes.
- the invention solves this problem by providing a flat tube with the features of claim 1 and a heat exchanger with the features of claim 5.
- the reversing bend section is formed such that in this area the transverse axis of the flat tube includes at most an angle of 45 ° with the planes which are parallel to a longitudinal and a transverse direction and perpendicular to a stacking direction.
- the longitudinal direction is defined by the course of the longitudinal axes of the flat pipe sections, while the stacking direction indicates the direction in which several flat pipes are arranged in succession when a heat exchanger pipe block is formed.
- the transverse direction represents the direction perpendicular to this longitudinal direction and to the stacking direction defined in this way. In general, the transverse direction defined in this way is parallel to the transverse axis direction of the planar pipe sections, but this is not mandatory, since alternatively the planar pipe sections can also be inclined with respect to this transverse direction if required .
- This inventive design of the reverse bend section ensures that its extension in the stacking direction can be kept significantly smaller than the flat tube width. Accordingly, the gaps between adjacent flat tubes do not need to be kept as large or 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 reversing 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.
- flat tube is bent such that the flat tube sections connected via a respective reversing bend section lie in the same or different longitudinal planes which are parallel to one another or inclined to one another by a predeterminable tilting angle, and in each case preferably with a mutual distance in the transverse direction between 0.2mm and 20mm.
- a tube block can be formed with a depth that corresponds to twice the flat tube width plus the said distance between the flat tube sections. With flat tubes bent several times in this way, the depth of the tube block per reversing bend section increases by the width of the flat tube plus the said transverse spacing of the flat tube sections.
- a flat tube further developed according to claim 3 forms a serpentine flat tube, in that at least one of the two flat tube parts connected via a reversing bend section is bent in the stacking direction to form a tubular serpentine, ie it consists of serpentine turns which follow one another in the stacking 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 narrow arrangement of associated collecting and distribution channels, which extend in the stacking direction on the relevant tube block side, in the depth direction of a tube block constructed therewith.
- the heat exchanger according to claim 5 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, hereinafter referred to collectively as the collecting channels for the sake of simplicity, are located on opposite tube block sides.
- the collecting channels can then each be formed by a collecting box or collecting tube, which run along the stacking direction on the relevant tube block side, also referred to as the vertical direction of the block, and the parallel supply or discharge of the temperature control medium passed through the tube interior to and from the individual flat tubes serve.
- the flat tube ends all open on the same tube block side.
- the two tube ends of each flat tube are offset from one another in the block depth direction, so that two collecting channels which are adjacent to one another in the block depth direction can be assigned to them.
- the temperature control medium passed through the interior of the pipe is supplied and removed on the same heat exchanger side.
- these collecting ducts 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.
- a group-wise serial flow through the flat tubes in the tube block is thereby achieved in that the temperature control medium supplied to the tube block via a first collecting channel of the cross-divided collecting tube or the cross-divided hollow chamber is initially only fed into the part of all flat tubes opening there.
- the collecting duct, into which this part of the flat tubes opens with the other tube end, then acts as a deflection channel, in which the temperature control medium is deflected from the flat tubes opening there into a further part of all flat tubes also opening there with one end.
- 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.
- Fig. 1 is a plan view of a flat tube with a reverse bend section and twisted. Pipe ends,
- FIG. 2 is a side view along the arrow II of FIG. 1,
- FIGS. 1 and 2 show a partial side view of a tube / fin block of an evaporator constructed from flat tubes according to FIGS. 1 and 2,
- FIG. 4 is a side view along arrow IV of FIG. 3,
- 5 shows a partial side view of a tube / fin block of an evaporator with serpentine flat tubes
- 6 is a side view along arrow VI of FIG. 5
- Fig. 7 is a schematic representation of a flat tube with two reverse bend sections and
- Fig. 8 is a cross-sectional view through e.g. 5 usable two-chamber manifold.
- 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, straight pipe sections e 2a, 2b, which are connected to one another via an inverted bend section 3 and opposite flow directions for a temperature control medium passed through the several parallel chambers inside the flat tube 1, e.g. a refrigerant of a motor vehicle air conditioning system.
- a temperature control medium passed through the several parallel chambers inside the flat tube 1, e.g. 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 flat, straight pipe sections 2a, 2b running parallel to the flow directions 4a, 4b define a longitudinal direction x and are offset from one another in a transverse direction y perpendicular thereto.
- both flat pipe sections 2a, 2b lie in a common xy plane, which is perpendicular to a stacking direction z, in which a plurality of such flat pipes are stacked to form a heat exchanger pipe block, as shown below 3 and 4 explained in more detail.
- FIGS. 1 to 6 each show the corresponding coordinate axes x, y, z.
- the reversing bend section 3 is obtained in that the initial, straight flat tube profile of a desired width b is kept at half its length and both tube halves are each turned over at a 90 ° angle, so that they run parallel to each other perpendicular to their original longitudinal direction and in this way form the two straight pipe sections 2a, 2b of the finished flat pipe 1.
- the bending process takes place in such a way that the two straight pipe sections 2a, 2b lying in one plane lie opposite one another with a distance a which can be selected depending on the application and which is preferably between approximately 0.2 mm and 20 mm, while the flat pipe width b is typically between one and a few Centimeters.
- While the straight pipe sections 2a, 2b are connected to one another via the reversing bend section 3, they both open 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 longitudinal axis parallel to it, i.e. with a transverse offset with respect to the longitudinal central axis, by any angle between 0 ° and 90 °, the torsion angle being approximately 60 ° in the case shown, as can be seen particularly clearly from FIG. 4.
- the transverse direction y is defined by being perpendicular to both the longitudinal direction x of the straight pipe sections and the pipe block stacking direction z.
- FIGS. 3 and 4 show an application for the flat tube type of FIGS. 1 and 2 in the form of a tube / fin block of an evaporator, as can be used in particular in motor vehicle air conditioning systems. It goes without saying that, depending on the design, the detail of the heat exchanger shown can also be used for any other heat transfer purposes.
- this evaporator contains between two end cover plates 9, 10 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 thus significantly smaller than the flat tube width b.
- the use of the flat tube of FIGS. 1 and 2 forms a tube-fin block with a two-part structure in depth, ie in the y direction, the tube sections in each of the two block parts same flow direction in the stacking direction z one above the other. Between the two block parts there is a distance a between the two straight lines Pipe sections 2a, 2b of each flat tube 1 corresponding gap is formed.
- the corrugated fins 8 extend in one piece over the entire flat tube depth and thus also over this gap, whereby they can protrude on both sides, ie on the front and on the back of the block, as required.
- the front of the block is defined by the fact that a second temperature control medium, for example supply air to be cooled for a vehicle interior, which flows outside the evaporator surfaces, flows in the pipe transverse direction y, ie in the block depth direction.
- the transverse extension d of the ends of the flat tube ends is less than the flat tube width b due to their twisting.
- This facilitates the connection of two associated collecting channels, not shown in FIGS. 3 and 4.
- these can e.g. each be formed by a header or header, the transverse extent of which does not need to be greater than the flat tube width b in the y-direction and, in its diameter, with a torsion angle of the flat tube ends of approximately 90 °, even needs to be only slightly greater than the flat tube thickness . It is therefore easily possible to arrange two header pipes on the relevant pipe block side lying side by side in the stacking direction z in order to accommodate one of the two ends of each flat pipe 1.
- a common collector pipe can be provided for both rows of stacks of pipe ends 6a, 6b, which is divided into the two required, separate collector channels by means of a longitudinal partition.
- the twisting of the tube ends shown in the example by approximately 60 ° makes it possible that the relatively close succession of the single-layer flat tubes 1 in the stack with the said stack height c, which is smaller than the flat tube width b, is not impeded.
- the evaporator with the tube / fin block formed in this way can be realized in a compact design and very pressure-stable and has a high heat transfer efficiency.
- Two pipe sections 2a, 2b offset in the block depth can be achieved with relatively narrow flat pipes, a heat transfer performance for which otherwise at least approximately twice as wide, non-bent flat pipes would be required.
- 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.
- FIG. 5 shows one of several flat serpentine tubes 11, which are stacked in any desired number to form the serpentine tube block there.
- the serpentine flat tube 11 used for this is largely identical in construction to that of FIGS. 1 and 2, with the exception that on both sides of the reversing bend section 3 ′ which is similar to that of FIGS. 1 and 2, not only a straight, single-layer pipe section, Instead, a multiple serpentine-shaped coil section 12a, 12b connects, which in turn are offset by a corresponding gap in the block depth direction, as can be seen more clearly from FIG. 6.
- the serpentine windings 13 of the respective coil section 12a, 12b are formed, as usual, by bending the flat tube at the relevant point around the transverse tube axis there by an angle of 180 °. Between the individual coil windings 13 and between successive serpentine flat tubes 11 there are heat-conducting corrugated fins 14 running from the front of the block to. Block back introduced with optional overhang. It is understood that here, as in the example of FIGS. 3 and 4, a corrugated fin row can instead be provided for each of the two rows of pipe blocks offset in the block depth direction, 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 are of course used in each corrugated fin layer, e.g. a first corrugated fin extending over two thirds of the tube block depth and a second 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 14 and thus the stacking distance of adjacent, straight flat tube sections both within a serpentine flat tube 11 and between two adjacent serpentine flat tubes corresponds approximately to that of the flat tube width in this example as well b significantly lower height c of the reversing arch section 3 '.
- the twisting chosen in this case of the flat tube ends 15a, 15b of 90 °, which in turn opens on the same block side, does not collide with this low stacking height, since the serpentine flat tubes, due to their coil sections 12a, 12b, each have a greater height in the stacking direction z than the flat tube width.
- FIG. 5 shows such a collecting tube 16 on the front side, into which the front row of the flat tube ends opens, while this and the parallel collecting tube for the rear row of the flat tube ends in FIG. 6 are not shown for the sake of clarity.
- the evaporator in serpentine construction according to FIGS. 5 and 6 has the reversing bend section 3 'on the same tube block side as the twisted tube ends 15a, 15b.
- the interposed serpentine coils 13 prevent the stacking not following twisted pipe ends 15a, 15b and reversing bend sections 3 '.
- the flat tube can thus have two or more reversing bend sections and corresponding deflections.
- An example with two successive reversing bend sections 17, 18 is shown schematically in FIG. 7 using the associated flow path.
- a first rectilinear tube section 20 extends from a flat tube end 19 to the opposite first reversing arc section 17, where it merges into a returning, second rectilinear flat tube section 21, which at the opposite second reversing arc section 18 merges into a third rectilinear tube section 22, which extends to the other flat tube end 23 extends.
- This flat tube is therefore suitable for the construction of a three-part heat exchanger tube block in a single-layer construction, i.e.
- the straight pipe sections 20, 21, 22 are essentially in a block plane.
- the two ends 19, 23 of each flat tube open out on opposite sides of the block, on which a collecting tube is thus to be arranged.
- the serpentine flat tube 11 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 flat tube end in question to lie on the block side opposite the reversing bend section.
- a serpentine flat tube of the type shown in FIG. 5, but with one or more additional reversing bend sections can be provided. can be seen in order to build up a tube block for a serpentine heat exchanger at least three parts in the block depth direction analogously to this, for example from FIG. 7.
- the flat tube ends can also be left undordied.
- a two-chamber header tube can be used, which already in the production stage has two separate, longitudinal tubes Has hollow chambers.
- a manifold 24 is shown in cross section in FIG. 8. It is made from an extruded profile and integrally contains two longitudinal chambers 25, 26 which are separate from one another and which form the collecting channels for the heat exchanger in question.
- suitable circumferential slots have to be made in the manifold 24, into which the flat tube ends are tightly inserted.
- header pipes can also be used which, by means of corresponding transverse walls, contain several header channels separated from each other in the block vertical direction z.
- 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 tempering medium flows from an inlet-side collecting duct into the group of flat tubes opening there and then arrives at the other end thereof in a collecting duct functioning as a deflection space, into which a second flat tube group opens in addition to this first group, into which the tempering medium is then deflected.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19830863A DE19830863A1 (de) | 1998-07-10 | 1998-07-10 | Flachrohr mit Querversatz-Umkehrbogenabschnitt und damit aufgebauter Wärmeübertrager |
DE19830863 | 1998-07-10 | ||
PCT/DE1999/002125 WO2000003190A1 (de) | 1998-07-10 | 1999-07-09 | Flachrohr mit querversatz-umkehrbogenabschnitt und damit aufgebauter wärmeübertrager |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1036296A1 true EP1036296A1 (de) | 2000-09-20 |
EP1036296B1 EP1036296B1 (de) | 2004-01-02 |
Family
ID=7873567
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99945947A Expired - Lifetime EP1036296B1 (de) | 1998-07-10 | 1999-07-09 | Flachrohr mit querversatz-umkehrbogenabschnitt und damit aufgebauter wärmeübertrager |
Country Status (6)
Country | Link |
---|---|
US (1) | US6546999B1 (de) |
EP (1) | EP1036296B1 (de) |
JP (1) | JP2002520570A (de) |
AU (1) | AU5849199A (de) |
DE (1) | DE19830863A1 (de) |
WO (1) | WO2000003190A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018039680A1 (en) * | 2016-08-26 | 2018-03-01 | Inertech Ip Llc | Cooling systems and methods using single-phase fluid and a flat tube heat exchanger with counter-flow circuiting |
Families Citing this family (42)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10146824A1 (de) * | 2001-09-18 | 2003-04-24 | Behr Gmbh & Co | Wärmeübertrager-Flachrohrblock mit umgeformten Flachrohrenden |
US20050011637A1 (en) * | 2001-11-08 | 2005-01-20 | Akihiko Takano | Heat exchanger and tube for heat exchanger |
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 |
US7650935B2 (en) * | 2001-12-21 | 2010-01-26 | Behr Gmbh & Co. Kg | Heat exchanger, particularly for a motor vehicle |
CN100533043C (zh) * | 2002-07-26 | 2009-08-26 | 贝洱两合公司 | 热交换装置 |
JP2005533995A (ja) * | 2002-07-26 | 2005-11-10 | ベール ゲーエムベーハー ウント コー カーゲー | 熱交換装置 |
CN1711456A (zh) * | 2002-11-07 | 2005-12-21 | 贝洱两合公司 | 热交换装置 |
DE10306848A1 (de) | 2003-02-18 | 2004-08-26 | Behr Gmbh & Co. Kg | Flachrohr mit Umkehrbogenabschnitt und damit aufgebauter Wärmeübertrager |
DE10351138B4 (de) * | 2003-11-03 | 2005-10-06 | Daimlerchrysler Ag | Verfahren zur Herstellung eines länglichen hohlen Bauteils mit einem Anlagebauteil |
JP2005188849A (ja) * | 2003-12-26 | 2005-07-14 | Zexel Valeo Climate Control Corp | 熱交換器 |
DE102004002252B4 (de) * | 2004-01-08 | 2006-10-26 | Visteon Global Technologies, Inc., Dearborn | Wärmeübertrager für Fahrzeuge |
US7322404B2 (en) * | 2004-02-18 | 2008-01-29 | Renewability Energy Inc. | Helical coil-on-tube heat exchanger |
US7281387B2 (en) * | 2004-04-29 | 2007-10-16 | Carrier Commercial Refrigeration Inc. | Foul-resistant condenser using microchannel tubing |
US7104314B2 (en) * | 2004-06-29 | 2006-09-12 | Modine Manufacturing Company | Multi-pass heat exchanger |
US7874349B2 (en) * | 2006-03-16 | 2011-01-25 | Visteon Global Technologies, Inc. | Heat exchanger tank |
DE102006018688B4 (de) * | 2006-04-13 | 2009-08-27 | Visteon Global Technologies Inc., Van Buren | Verfahren zum Biegen von Multiportrohren für Wärmeübertrager |
FR2899959B1 (fr) * | 2006-04-14 | 2008-08-08 | Valeo Systemes Thermiques | Echangeur de chaleur ameliore et module d'echange de chaleur comportant un tel echangeur |
US7921904B2 (en) * | 2007-01-23 | 2011-04-12 | Modine Manufacturing Company | Heat exchanger and method |
US8480651B2 (en) | 2007-08-02 | 2013-07-09 | Covidien Lp | Cannula system |
JP2009216315A (ja) * | 2008-03-11 | 2009-09-24 | Showa Denko Kk | 熱交換器 |
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 |
ATE554361T1 (de) * | 2009-04-28 | 2012-05-15 | Abb Research Ltd | Wärmerohr mit gewundenem rohr |
EP2246654B1 (de) * | 2009-04-29 | 2013-12-11 | ABB Research Ltd. | Mehrreihiger Thermosyphon-Wärmetauscher |
US20120097381A1 (en) * | 2009-06-22 | 2012-04-26 | Meidensha Corporation | Heat sink |
JP2011099630A (ja) * | 2009-11-06 | 2011-05-19 | Mitsubishi Electric Corp | 熱交換器及びこの熱交換器を用いた冷蔵庫、空気調和機 |
DE102009047620C5 (de) * | 2009-12-08 | 2023-01-19 | Hanon Systems | Wärmeübertrager mit Rohrbündel |
DE102010032899A1 (de) * | 2010-07-30 | 2012-02-02 | Valeo Klimasysteme Gmbh | Kühlvorrichtung für eine Fahrzeugbatterie sowie Fahrzeugbatteriebaugruppe mit einer solchen Kühlvorrichtung |
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 |
DE102012222664A1 (de) * | 2012-08-09 | 2014-03-06 | Behr Gmbh & Co. Kg | Kondensator |
US20140182827A1 (en) * | 2012-11-30 | 2014-07-03 | Carlos Quesada Saborio | Tubing Element for a Heat Exchanger |
US9341418B2 (en) * | 2013-03-01 | 2016-05-17 | International Business Machines Corporation | Thermal transfer structure with in-plane tube lengths and out-of-plane tube bend(s) |
US9891007B2 (en) * | 2013-03-21 | 2018-02-13 | Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. | Bent heat exchanger and method for manufacturing the same |
US10247482B2 (en) * | 2013-12-13 | 2019-04-02 | Hangzhou Sanhua Research Institute Co., Ltd. | Bent heat exchanger and method for bending the heat exchanger |
DE102014206612A1 (de) * | 2014-04-04 | 2015-10-29 | Mahle International Gmbh | Wärmetauscher |
KR20170087920A (ko) * | 2014-11-25 | 2017-07-31 | 사파 에이에스 | 멀티 포트 압출 튜브 구성 |
US11193715B2 (en) | 2015-10-23 | 2021-12-07 | Hyfra Industriekuhlanlagen Gmbh | Method and system for cooling a fluid with a microchannel evaporator |
US10619932B2 (en) | 2015-10-23 | 2020-04-14 | Hyfra Industriekuhlanlagen Gmbh | System for cooling a fluid with a microchannel evaporator |
CN106642826B (zh) * | 2015-10-28 | 2019-04-19 | 丹佛斯微通道换热器(嘉兴)有限公司 | 换热器 |
WO2019011058A1 (zh) * | 2017-07-13 | 2019-01-17 | 杭州三花研究院有限公司 | 换热器 |
KR20190032106A (ko) * | 2017-09-19 | 2019-03-27 | 엘지전자 주식회사 | 냉장고용 응축기 |
US11226139B2 (en) | 2019-04-09 | 2022-01-18 | Hyfra Industriekuhlanlagen Gmbh | Reversible flow evaporator system |
US20220221226A1 (en) * | 2021-01-13 | 2022-07-14 | Mahle International Gmbh | Flat tube and heat exchanger |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3273227A (en) * | 1963-06-12 | 1966-09-20 | Olin Mathieson | Fabrication of heat exchange devices |
US3416600A (en) * | 1967-01-23 | 1968-12-17 | Whirlpool Co | Heat exchanger having twisted multiple passage tubes |
US4217953A (en) * | 1976-03-09 | 1980-08-19 | Nihon Radiator Co. Ltd. (Nihon Rajiecta Kabushiki Kaisha) | Parallel flow type evaporator |
DE2907810C2 (de) * | 1979-02-28 | 1985-07-04 | MTU Motoren- und Turbinen-Union München GmbH, 8000 München | Wärmetauscher zur Führung von Gasen stark unterschiedlicher Temperaturen |
IT1234289B (it) * | 1989-06-14 | 1992-05-14 | Piemontese Radiatori | Perfezionamenti apportati ad uno scambiatore di calore a tubi appiattiti |
US5036909A (en) * | 1989-06-22 | 1991-08-06 | General Motors Corporation | Multiple serpentine tube heat exchanger |
US5099576A (en) * | 1989-08-29 | 1992-03-31 | Sanden Corporation | Heat exchanger and method for manufacturing the heat exchanger |
JPH04177094A (ja) * | 1990-11-13 | 1992-06-24 | Sanden Corp | 積層型熱交換器 |
US5314013A (en) * | 1991-03-15 | 1994-05-24 | Sanden Corporation | Heat exchanger |
FR2712966B1 (fr) | 1993-11-24 | 1996-01-19 | Valeo Thermique Moteur Sa | Echangeur de chaleur à tubes plats, en particulier pour véhicule automobile. |
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 |
JPH09137245A (ja) * | 1995-11-09 | 1997-05-27 | Denso Corp | 熱交換器用アルミニウム管体および該アルミニウム管体を使用したアルミニウム製熱交換器 |
EP0845648B1 (de) * | 1996-11-27 | 2002-01-30 | Behr GmbH & Co. | Flachrohr-Wärmeübertrager, insbesondere Kondensator vom Serpentinentyp |
DE19729497A1 (de) * | 1997-07-10 | 1999-01-14 | Behr Gmbh & Co | Flachrohr-Wärmeübertrager |
-
1998
- 1998-07-10 DE DE19830863A patent/DE19830863A1/de not_active Ceased
-
1999
- 1999-07-09 JP JP2000559386A patent/JP2002520570A/ja active Pending
- 1999-07-09 WO PCT/DE1999/002125 patent/WO2000003190A1/de active IP Right Grant
- 1999-07-09 EP EP99945947A patent/EP1036296B1/de not_active Expired - Lifetime
- 1999-07-09 AU AU58491/99A patent/AU5849199A/en not_active Abandoned
-
2000
- 2000-03-10 US US09/523,386 patent/US6546999B1/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO0003190A1 * |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2018039680A1 (en) * | 2016-08-26 | 2018-03-01 | Inertech Ip Llc | Cooling systems and methods using single-phase fluid and a flat tube heat exchanger with counter-flow circuiting |
US11384989B2 (en) | 2016-08-26 | 2022-07-12 | Inertech Ip Llc | Cooling systems and methods using single-phase fluid |
EP4231796A3 (de) * | 2016-08-26 | 2023-11-29 | Inertech IP LLC | Kühlsysteme und verfahren mit einphasigem fluid und flachrohrwärmetauscher mit gegenstromschaltung |
US11940227B2 (en) | 2016-08-26 | 2024-03-26 | Inertech Ip Llc | Cooling systems and methods using single-phase fluid |
Also Published As
Publication number | Publication date |
---|---|
EP1036296B1 (de) | 2004-01-02 |
WO2000003190A1 (de) | 2000-01-20 |
JP2002520570A (ja) | 2002-07-09 |
AU5849199A (en) | 2000-02-01 |
US6546999B1 (en) | 2003-04-15 |
DE19830863A1 (de) | 2000-01-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1036296B1 (de) | Flachrohr mit querversatz-umkehrbogenabschnitt und damit aufgebauter wärmeübertrager | |
EP2026028B1 (de) | Wärmeübertrager, insbesondere für ein Kraftfahrzeug | |
EP1042641B1 (de) | Wärmeübertragender rohrblock und dafür verwendbares mehrkammer-flachrohr | |
EP0401752B1 (de) | Verflüssiger für ein Kältemittel einer Fahrzeugklimaanlage | |
DE3650658T2 (de) | Wärmetauscher | |
DE69219107T2 (de) | Verdampfer | |
DE3780648T2 (de) | Kondensator. | |
DE60011616T2 (de) | Wärmetauscher mit mehrkanalrohren | |
EP0845647B1 (de) | Flachrohr-Wärmeübertrager mit tordiertem Flachrohrendabschnitt | |
DE102006029378B4 (de) | Flachrohr für Wärmetauscher und Herstellungsverfahren | |
EP1597529B1 (de) | Flachrohr mit umkehrbogenabschnitt und damit aufgebauter w r me bertrager | |
DE69729836T2 (de) | Verdampfer | |
DE10054158A1 (de) | Mehrkammerrohr mit kreisförmigen Strömungskanälen | |
DE10257767A1 (de) | Wärmeübertrager | |
EP1411310B1 (de) | Wärmeübertrager in Serpentinenbauweise | |
DE10150213A1 (de) | Stranggepreßtes Profil, insbesondere für Wärmetauscher | |
EP0845648B1 (de) | Flachrohr-Wärmeübertrager, insbesondere Kondensator vom Serpentinentyp | |
EP1588115A1 (de) | Wärmeübertrager, insbesondere gaskühler | |
EP2937658B1 (de) | Innerer wärmeübertrager | |
EP1923654B1 (de) | Wärmeübertrager | |
EP1321734A1 (de) | Flachrohr-Wärmeübertrager sowie Herstellungsverfahren hierfür | |
EP1166025B1 (de) | Mehrblock-wärmeübertrager | |
EP1293743B1 (de) | Wärmeübertrager-Flachrohrblock mit umgeformten Flachrohrenden | |
DE202019103964U1 (de) | Wärmeaustauscher |
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: 20000720 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE |
|
17Q | First examination report despatched |
Effective date: 20020313 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
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): ES FR GB IT SE |
|
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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED. Effective date: 20040102 Ref country code: FR 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: 20040102 |
|
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: IE Ref legal event code: FG4D Free format text: GERMAN |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20040218 |
|
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: 20040402 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20040413 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FD4D |
|
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 |
|
26N | No opposition filed |
Effective date: 20041005 |
|
EN | Fr: translation not filed | ||
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20050627 Year of fee payment: 7 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20060709 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20060709 |