EP1664655B1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- EP1664655B1 EP1664655B1 EP04763801A EP04763801A EP1664655B1 EP 1664655 B1 EP1664655 B1 EP 1664655B1 EP 04763801 A EP04763801 A EP 04763801A EP 04763801 A EP04763801 A EP 04763801A EP 1664655 B1 EP1664655 B1 EP 1664655B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fluid
- heat exchanger
- flow
- corrugated
- flat tubes
- 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
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- 239000012530 fluid Substances 0.000 claims abstract description 99
- 238000001816 cooling Methods 0.000 claims abstract description 23
- 210000002816 gill Anatomy 0.000 claims description 58
- 239000003570 air Substances 0.000 description 47
- 239000002245 particle Substances 0.000 description 6
- 238000004088 simulation Methods 0.000 description 4
- 238000003491 array Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000010276 construction Methods 0.000 description 3
- 239000002826 coolant Substances 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 239000003507 refrigerant Substances 0.000 description 3
- 238000005096 rolling process Methods 0.000 description 3
- 241001295925 Gegenes Species 0.000 description 2
- 239000000110 cooling liquid Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- -1 for example Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 241000446313 Lamella Species 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000009969 flowable effect Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
Definitions
- the invention relates to a heat exchanger, in particular for motor vehicles.
- Such a heat exchanger can be designed, for example, as an integrated heat exchanger with a condenser of an air conditioning system and a coolant radiator for motor vehicles.
- the heat exchanger usually has a number of juxtaposed, parallel to each other extending flat tubes in several rows. In these rows of flat tubes flow first fluids, in the above example, a refrigerant and a coolant.
- the flat tubes are connected to manifolds and manifolds and exposed to the flow of a second fluid, such as ambient air, to effect heat transfer between the fluids. Between the individual, spaced-apart flat tubes flow paths for the second fluid are formed.
- Another heat exchanger with cooling fins is for example from the US 4,676,304 known.
- the cooling fins are substantially parallel to the flow direction of the second fluid (here: air).
- the second fluid here: air
- This problem is particularly significant when the heat exchanger in the direction of flow of the second fluid has small dimensions. In this case, a high mass flow rate of the second fluid does not necessarily cause a high heat transfer performance.
- the available temperature difference between the first and the second fluid is used only to a relatively small extent.
- the invention has for its object to provide a heat exchanger of the type mentioned with cooling fins, which are designed streamlined and at the same time reduce a thermal coupling between a plurality of first fluids.
- a heat exchanger having the features of claim 1.
- the heat exchanger of first fluids through flowable flat tubes, which are arranged in at least two rows, and the outside are acted upon by a second fluid and substantially transversely to the flow direction of Second fluid are arranged parallel to each other such that flow paths are formed for the second fluid, in which cooling fins are arranged, each extending between adjacent flat tubes.
- the cooling fins are in this case formed as corrugated fins, wherein a plurality of corrugated fins are arranged one behind the other in the flow direction of the second fluid and these laterally, that are offset in the flow direction of the first fluid to each other.
- a very high proportion of the second fluid flowing through the heat exchanger is used for heat transfer.
- an overall higher mass flow of the second fluid flows through gills located in the area of the second fluid downstream side of a rib than without the offset between the corrugated fins. This may cause increased heat transfer performance in this area.
- a temperature boundary layer which optionally forms on a pipe wall, influenced, so that under certain circumstances, a heat transfer from the pipe wall to the second fluid or vice versa is increased.
- corrugated fins Due to the staggered arrangement of the corrugated fins is at the same time an undesirable heat transfer between different rows of tubes on the corrugated fins reduced, although the ribs are formed from a common band. This is in turn advantageous in production terms, since several successively arranged, formed from a common band, that is integral corrugated fins are easy to insert between the rows of tubes of the heat exchanger.
- the corrugated ribs including the gills are in particular produced by rolling from a metal strip.
- a streamlined design of the corrugated fins is preferably achieved in that their surfaces are substantially parallel to the flow direction of the second fluid, i. the surface normals of the corrugated fins are substantially at right angles to the flow direction of the second fluid.
- the aerodynamic design of the corrugated fins is ensured by the lateral offset successively arranged corrugated fins that only a smaller proportion of the second fluid unused, i. without appreciable heat transfer, flows between the flat tubes than without such an offset.
- This advantage is more pronounced the higher the rib spacing b between two ribs.
- two or three similarly shaped corrugated ribs are offset from each other in succession.
- the individual corrugated fins are preferably directly adjacent to each other, i. arranged without a distance in the flow direction of the second fluid. As a result, a large heat exchanger surface is given.
- a spaced arrangement of the narrower in this case corrugated fins be provided.
- the corrugated fins also have gills for guiding the second fluid.
- gills for guiding the second fluid.
- all the gills of a rib section enclosed between two flat tubes of a corrugated fin are inclined in the same direction with respect to the flow direction of the second fluid.
- a similar inclination of the gills within a rib section has the advantage that, if appropriate, the flow can be directed to a downstream rib section.
- the gills offset successively arranged rib portions are oppositely inclined, so that the heat exchanger through the flowing second fluid is given a longer flow path.
- the gills of two adjacent gill panels can also be placed obliquely in the same direction, it may then be advantageous if the gills of the two adjacent gill panels upstream or downstream gills are inclined in opposite directions to the gills of the two adjacent gill panels.
- Uniform coverage of the flow cross-section through which the second fluid flows is preferably achieved by displaced rib sections arranged one behind the other running parallel to one another.
- the mutually offset rib sections are preferably perpendicular to the flat tubes. If the rib surfaces deviate slightly (up to about 6 degrees) from the parallelism, in which case they are still to be regarded as substantially parallel in the context of the invention, the thermodynamic advantages of the mutually offset ribs are scarcely impaired as a result. Likewise, the use of so-called V-ribs or even arbitrarily rounded ribs is conceivable.
- the rib geometry according to the invention is particularly applicable to automotive heat exchangers such as coolant radiators, radiators, condensers and evaporators.
- the depth Kiement LP LP in the range of 0.7 to 3 mm at a gill angle of 20 to 30 degrees performance, because thereby the flow angle, i. the deflection of the second fluid is increased from one channel to the adjacent, which in turn results in a longer flow path for the second fluid.
- the rib height for such a system is advantageously in the range of 4 to 12 mm.
- the rib density for this system is advantageously in the range of 40 to 85 Ri / dm, which corresponds to a rib spacing or a rib pitch of 1.18 to 2.5 mm.
- the Fig. 1 a, 1 b and 2a, 2b show a detail of a heat exchanger 1 with parallel arranged flat tubes 2, which are flowed through by a first fluid FL1a in a first flow direction S1.
- the flat tubes 2 are equipped with flow guide 2a and connected to (not shown) manifolds or manifolds.
- the fluid FL1a is for example a cooling liquid or a refrigerant condensing in the heat exchanger 1.
- Corrugated fins 3 arranged as cooling fins. Embodiments with a higher number of corrugated fins 3 are also feasible.
- the corrugated fins 3 are meander-shaped bent from a metal sheet, with each one adjacent to a flat tube 2 rib section 4a with a two adjacent flat tubes 2 connecting rib section 4b alternates.
- the voltage applied to the flat tubes 2 rib portions 4a are thermally conductively connected to the flat tubes 2, in particular soldered.
- the two adjacent flat tubes 2 connecting rib sections 4b are perpendicular to the flat tubes 2 and form flow paths for a second fluid FL2, for example, air, which flows through the heat exchanger 1 in the flow direction S2.
- the second fluid FL2 flows substantially parallel to the surface 5 of the corrugated fins 3, ie, the second fluid FL2 initially encounters only the narrow end faces 6 of the corrugated fins 3 when flowing into the heat exchanger 1.
- the second fluid FL2 can thereby heat exchanger 1 at high speed and flow through correspondingly high mass flow rate.
- Two corrugated fins 3 arranged one behind the other between two flat tubes 2 are offset from one another by half the width b between adjacent fin sections 4b.
- an offset of b / 3 can also be selected, wherein other values for the offset are also conceivable.
- Two or three adjacent corrugated fins 3, which extend across the depth T of the heat exchanger 1, are produced by rolling from a belt 8.
- the band 8 is in the range of the respective offset between the two ( Fig. 1a, 1b . Fig. 3 ) or three ( Fig. 2a, 2b . Fig. 4 )
- Corrugated ribs 3 cut and cut the gills 7 in the corrugated fins 3.
- Offset or higher-order offset ( Fig. 5e, 5f, 5g ) of the corrugated fins 3 is alternatively produced by the same type of separate corrugated fins 3 are arranged with an offset between 0.1 mm and b / 2, where b is the distance between two adjacent flat tubes 2.
- FIG. 5d is disturbed by the downstream of the flow direction S2 corrugated fin 3, so that an increase in the temperature gradient is generated, which causes an increase in the heat transfer.
- a heat exchanger 1 with a shallow depth T of, for example, 12 to 20 mm, a highly effective heat transfer between the second fluid FL2 and the first fluid FL1 a is given.
- Fig. 5 shows corrugated fins 10a, b .., l, each with a plurality of gill fields in cross-sectional view.
- cooling fins with flow-guiding lamellae (gills) in the individual fins is usually a rib between two tubes in the main flow direction of the second fluid exclusively in a plane without offset ( Fig. 5a, 5b ).
- These cooling fins have at least two so-called gill panels 11, 12 and 13, 14, which are separated by a web of different design.
- the orientation of the flow-conducting lamellae (gills) of adjacent gill fields is usually in opposite directions.
- corrugated fins can also two, three or more similarly shaped corrugated fins (cooling fins) offset from each other to be arranged one behind the other, ie, the one corrugated fin with flow-conducting fins (gills) can be offset in several planes to each other.
- the number of corrugated fins, which are arranged one behind the other viewed in the direction of flow of the second fluid, depending on the depth of the heat exchanger and / or the depth of the corrugated fins are selected.
- 2, 3 or more rows can be used; for example, 2, 3, 4 or more rows can be used for a depth of up to 24 mm; for example, 2, 3 can be used for a depth of up to 30 mm , 4, 5 or more rows are used, with a construction depth of up to 36 mm, for example, 2, 3, 4, 5, 6 or more rows can be used, with a construction depth of up to 42 mm, for example, 2, 3, 4, 5, 6, 7 or more rows can be used, with a depth up to 48 mm, for example, 2, 3, 4, 5, 6, 7, 8 or more rows can be used, with a depth
- 2, 3, 4, 5, 6, 7, 8, 9 or more rows can be used up to 54 mm, for example 2, 3, 4, 5, 6, 7, 8, 9, for a construction depth of up to 60 mm, 10 or more rows are used, with a depth up to 66 mm, for example, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11 or more rows can be used.
- An embodiment for 2 rows 15 and 16 shows Fig. 5c in a cross-sectional view.
- FIG. 5d An embodiment for 3 rows 17, 18 and 19 shows Fig. 5d in a cross-sectional view.
- An embodiment for 4 rows 20, 21, 22 and 23 shows Fig. 5e in a cross-sectional view.
- An embodiment for 5 rows 24, 25, 26, 27 and 28 shows Fig. 5f in a cross-sectional view.
- An embodiment for 5 rows 29, 30, 31, 32 and 33 shows Fig. 5g in a cross-sectional view.
- An embodiment for 5 rows 34, 35, 36, 37 and 38 shows Fig. 5h in a cross-sectional view.
- More than two mutually offset rows can preferably be distributed over a total of two mutually offset planes as in the embodiments in the Figures 5d, 5e and 5g , But they can also be distributed on three or more different levels as in the embodiments in the Figures 5f and 5h , where the distances between each two levels may be the same or different.
- the corrugated rib 10i or 10j has no gill. This embodiment also causes an influence of the temperature boundary layer on the tube walls and / or an improved flow through the lamellae.
- the gill panels 45, 46, 47 of the corrugated fin 10k may be different in size ( Fig. 5k ).
- an assignment of the gill panels 45, 46 of a first row of tubes and the gill panel 47 of a second row of tubes advantageous because the displacement 49 between the gill panels 46 and 47, a thermal connection between the rows of tubes is suppressed.
- a combination of different sized gill fields 65, 66, 67, 68, 69 in different planes is possible as in the corrugated fin 10l ( Fig. 5l ).
- the number of gills per row is for example between 2 and 30 gills depending on the number of rows and the depth of the heat exchanger.
- the number of gills per gill field from an engineering point of view in odd number of rows that is not identical at 3, 5, 7, 9 or 11 rows.
- the number of gills per gill panel can be identical, but this is not necessary.
- a corrugated fin in a row i. E. without offset, consisting of a row with two gill panels, which are separated by a ridge in the form of a roof, considered (prior art).
- a corrugated fin with 2 rows and a corrugated fin with 3 rows is considered.
- the simulation determines the mass flow through the individual fin openings as well as the radiation power from the pipe to the cooling air.
- Fig. 6 shows the flow field of the air at an air inlet velocity v air of 3 m / s in a heat exchanger 51 with corrugated fins 52, 53 under the boundary conditions described above in the area between two gill fields 54, 55 and 56, 57.
- the webs 58 and 59 between two Gill fields here have a roof shape.
- the arrows 60 show the main flow path of the air particles, which flow through the last fin opening 61 in front of the web 59, then undergo a flow deflection and flow through the fin openings 62, 63 in the adjacent gill field 57.
- the figure shows that only the second slat opening 62 of the gill field 57 is again flowed through by a larger number of air particles, whereby only the speed field through the third slat opening 63 corresponds approximately to the Geschwindkeitstruck in the previous gill field 56 again.
- Fig. 7 shows the flow field of the air at an air inlet velocity v air of 3 m / s in a heat exchanger 71 with corrugated fins 72, 73 under the The boundary conditions described above in the region of a displacement point 74 or 75 between two gill arrays 76, 77 and 78, 79.
- the arrows 80 show the main flow path of the air particles before the offset 75, on the one hand through the last slat opening 81 before the offset and on the other by the Displacement opening 75.
- the air particles undergo a flow deflection after the flow through the offset opening 75, wherein the air particles which flow through the offset opening, then flow mainly through the first and second fin opening 82, 83 of the adjacent gill field 79.
- FIG. 8 shows the percentage air mass flow in the two corrugated fin configurations with two or three rows (one or two offset points) always above 9%, whereas in corrugated fins in a plane / row of air mass flow at the two fin openings following the land area below 8% with a minimum of about 4% drops. If the air mass flow in the corrugated rib consisting of a plane in the Lammellenö réelle before the land area of about 12% to about 10%, then decreases in the corrugated rib consisting of two Plains / rows here the mass flow through the last slat opening in front of the offset point of about 12 to about 13%.
- FIG. 9 shows the percentage air mass flow in the two corrugated fin configurations with two or three rows (one or two offset points) always above 12%, whereas in corrugated ribs in a plane / row of air mass flow at the two lamellar openings subsequent to the land area under 11% with a minimum of about 4.5%. If the air mass flow at the corrugated rib consisting of a plane in the Lammellenö réelle before the web area of about 16.5% drops to about 15%; Thus, in the corrugated rib consisting of two levels / rows here increases the mass flow through the last slat opening in front of the offset point of about 16.5 to about 18%.
- the Fig. 10a, b and 11a, b each show a detail of a heat exchanger 1 according to the invention with in two rows 1a, b arranged parallel to each other flat tubes 2, which are flowed through by first fluids FL1a, b in a first flow direction S1.
- the flat tubes 2 are connected to (not shown) manifolds or manifolds.
- the fluids FL1a, b are, for example, a cooling liquid and a refrigerant condensing in the heat exchanger 1. It may as well be two identical fluids within a two- or more-row heat exchanger 1.
- Corrugated fins 3 arranged as cooling fins. Embodiments with a higher number of corrugated fins 3 are also feasible.
- the corrugated fins 3 are meander-shaped bent from a metal sheet, with each one adjacent to a flat tube 2 rib section 4a with a two adjacent flat tubes 2 connecting rib section 4b alternates.
- the voltage applied to the flat tubes 2 rib portions 4a are thermally conductively connected to the flat tubes 2, in particular soldered.
- the two adjacent flat tubes 2 connecting rib sections 4b are perpendicular to the flat tubes 2 and form flow paths for a second fluid FL2, for example, air, which flows through the heat exchanger 1 in the flow direction S2.
- the second fluid FL2 flows substantially parallel to the surface of the corrugated fins 3, ie, the second fluid FL2 strikes when entering the heat exchanger 1 initially only on the narrow end faces 6 of the corrugated fins 3.
- the second fluid FL2 can thereby the heat exchanger 1 at high speed and flow through correspondingly high mass flow rate.
- Gills 7 are formed out of the rib sections 4b and extend transversely to the flow direction S2 of the second fluid FL2 and transversely to the flow direction S1 of the first fluids FL1a, b.
- the gills 7 Within a rib section 4b, on the one hand, a particularly good heat transfer between the second fluid FL2 and this rib section 4b, on the other hand, a targeted conduction of the second fluid FL2 to the rib section 4b arranged obliquely behind in the flow direction S2. In this way, the mass flow of the second fluid FL2 flowing through the heat exchanger 1 is almost completely utilized with high utilization of the temperature difference between the first fluids FL1a, b and the second fluid FL2 for heat transfer.
- the corrugated fins 3 are offset from each other. Because of the one-piece design, the corrugated fins 3 of different rows of tubes are connected to one another via narrow webs 9a in the region of the rib sections 4a resting against the flat tubes 2. Since these webs 9a represent the only heat-conducting connection between the rows of tubes 1a, b, heat transfer from one row of tubes to the other is effectively suppressed.
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- Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
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- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Power Steering Mechanism (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Separation By Low-Temperature Treatments (AREA)
Abstract
Description
Die Erfindung betrifft einen Wärmetauschers, insbesondere für Kraftfahrzeuge.The invention relates to a heat exchanger, in particular for motor vehicles.
Ein derartiger Wärmetauscher kann beispielsweise als integrierter Wärmetauscher mit einem Kondensator einer Klimaanlage und einem Kühlmittel-Kühler für Kraftfahrzeuge ausgebildet sein. Der Wärmetauscher weist üblicherweise eine Anzahl nebeneinander angeordneter, parallel zueinander verlaufender Flachrohre in mehreren Reihen auf. In diesen Flachrohrreihen fließen erste Fluide, im obigen Beispiel ein Kältemittel und ein Kühlmittel. Die Flachrohre sind an Sammelleitungen oder Sammelrohre angeschlossen und der Strömung eines zweiten Fluids, beispielsweise Umgebungsluft, ausgesetzt, um einen Wärmeübergang zwischen den Fluiden zu bewirken. Zwischen den einzelnen, voneinander beabstandeten Flachrohren sind Strömungswege für das zweite Fluid ausgebildet.Such a heat exchanger can be designed, for example, as an integrated heat exchanger with a condenser of an air conditioning system and a coolant radiator for motor vehicles. The heat exchanger usually has a number of juxtaposed, parallel to each other extending flat tubes in several rows. In these rows of flat tubes flow first fluids, in the above example, a refrigerant and a coolant. The flat tubes are connected to manifolds and manifolds and exposed to the flow of a second fluid, such as ambient air, to effect heat transfer between the fluids. Between the individual, spaced-apart flat tubes flow paths for the second fluid are formed.
Zur Verbesserung der Wärmeübertragung zwischen den Fluiden sind zwischen den Flachrohren an diesen befestigte Kühlrippen angeordnet. Die Oberflächen der Kühlflächen liegen bei dem aus der
Ein weiterer Wärmetauscher mit Kühlrippen ist beispielsweise aus der
Bei integrierten Wärmetauschern tritt häufig das Problem auf, daß über eine gemeinsame Wellrippe, das heißt über einstückig ausgebildete Wellrippen der Einzelwärmetauscher, Wärme von einem Einzelwärmetauscher auf den anderen übertritt. Um diesen unerwünschten Wärmeübergang zu reduzieren, ist beispielsweise in der
Ein weiterer integrierter Wärmetauscher mit gemeinsamer Wellrippe ist aus der
Another integrated heat exchanger with common corrugated rib is from the
Der Erfindung liegt die Aufgabe zugrunde, einen Wärmetauscher der eingangs genannten Art mit Kühlrippen anzugeben, die strömungsgünstig gestaltet sind und zugleich eine thermische Kopplung zwischen mehreren ersten Fluiden reduzieren.The invention has for its object to provide a heat exchanger of the type mentioned with cooling fins, which are designed streamlined and at the same time reduce a thermal coupling between a plurality of first fluids.
Diese Aufgabe wird erfindungsgemäß gelöst durch einen Wärmetauscher mit den Merkmalen des Anspruchs 1. Hierbei weist der Wärmetauscher von ersten Fluiden durchströmbare Flachrohre auf, die in zumindest zwei Reihen angeordnet sind, und die außen mit einem zweiten Fluid beaufschlagbar sind und im Wesentlichen quer zur Strömungsrichtung des zweiten Fluids derart parallel zueinander angeordnet sind, dass für das zweite Fluid Strömungswege ausgebildet sind, in denen Kühlrippen angeordnet sind, die sich jeweils zwischen benachbarten Flachrohren erstrecken. Die Kühlrippen sind hierbei als Wellrippen ausgebildet, wobei in Strömungsrichtung des zweiten Fluids mehrere Wellrippen hintereinander angeordnet sind und diese seitlich, das heißt in Strömungsrichtung der ersten Fluide, zueinander versetzt sind. Durch die Versetzung hintereinander angeordneter Wellrippen wird ein sehr hoher Anteil des den Wärmetauscher durchströmenden zweiten Fluids zur Wärmeübertragung genutzt. Bei Wellrippen mit Kiemen strömt gegebenenfalls insgesamt ein höherer Massenstrom des zweiten Fluids durch Kiemen, die im Bereich der für das zweite Fluid stromabwärts liegenden Seite einer Rippe angeordnet sind, als ohne den Versatz zwischen den Wellrippen. Dies bewirkt gegebenenfalls eine erhöhte Wärmeübertragungsleistung in diesem Bereich. Desweiteren wird eine Temperaturgrenzschicht, die sich gegebenenfalls an einer Rohrwand ausbildet, beeinflußt, so daß unter Umständen ein Wärmetransport von der Rohrwand auf das zweite Fluid oder umgekehrt erhöht wird. Durch die versetzte Anordnung der Wellrippen wird gleichzeitig ein unerwünschter Wärmeübertrag zwischen verschiedenen Rohrreihen über die Wellrippen reduziert, obwohl die Rippen aus einem gemeinsamen Band gebildet sind. Dies ist wiederum in fertigungstechnischer Sicht vorteilhaft, da mehrere hintereinander angeordnete, aus einem gemeinsamen Band gebildete, das heißt einstückige Wellrippen einfach zwischen die Rohrreihen des Wärmetauschers einsetzbar sind. Die Wellrippen einschließlich der Kiemen sind insbesondere durch Walzen aus einem Metallband herstellbar.This object is achieved by a heat exchanger having the features of
Eine strömungsgünstige Gestaltung der Wellrippen wird bevorzugt dadurch erreicht, dass deren Oberflächen im Wesentlichen parallel zur Strömungsrichtung des zweiten Fluids liegen, d.h. die Flächennormalen der Wellrippen im Wesentlichen einen rechten Winkel mit der Strömungsrichtung des zweiten Fluids einschließen. Trotz dieser strömungsgünstigen Ausbildung der Wellrippen ist durch den seitlichen Versatz hintereinander angeordneter Wellrippen sichergestellt, dass nur ein geringerer Anteil des zweiten Fluids ungenutzt, d.h. ohne nennenswerte Wärmeübertragung, zwischen den Flachrohren hindurchströmt als ohne einen solchen Versatz. Dieser Vorteil tritt umso deutlicher in Erscheinung, je höher der Rippenabstand b zwischen zwei Rippen ist. Vorzugsweise sind zwei oder drei gleichartig geformte Wellrippen versetzt zueinander hintereinander angeordnet. Um eine hohe Wärmeübertragungsleistung zu gewährleisten, sind die einzelnen Wellrippen vorzugsweise direkt aneinander grenzend, d.h. ohne Abstand in Strömungsrichtung des zweiten Fluids, angeordnet. Hierdurch ist eine große Wärmetauscherfläche gegeben. Alternativ hierzu kann, um den Strömungswiderstand zu reduzieren, eine beabstandete Anordnung der in diesem Fall schmaleren Wellrippen vorgesehen sein.A streamlined design of the corrugated fins is preferably achieved in that their surfaces are substantially parallel to the flow direction of the second fluid, i. the surface normals of the corrugated fins are substantially at right angles to the flow direction of the second fluid. Despite this aerodynamic design of the corrugated fins is ensured by the lateral offset successively arranged corrugated fins that only a smaller proportion of the second fluid unused, i. without appreciable heat transfer, flows between the flat tubes than without such an offset. This advantage is more pronounced the higher the rib spacing b between two ribs. Preferably, two or three similarly shaped corrugated ribs are offset from each other in succession. In order to ensure a high heat transfer performance, the individual corrugated fins are preferably directly adjacent to each other, i. arranged without a distance in the flow direction of the second fluid. As a result, a large heat exchanger surface is given. Alternatively, in order to reduce the flow resistance, a spaced arrangement of the narrower in this case corrugated fins be provided.
Die Wellrippen weisen ferner Kiemen zur Lenkung des zweiten Fluids auf. Durch eine sich an den Kiemen ausbildende sogenannte Anlaufströmung, die in einem Bereich der Wellrippe einen hohen Temperaturgradienten aufweist, ist eine verbesserte Wärmeübertragung zwischen dem zweiten Fluid und den Wellrippen sichergestellt.The corrugated fins also have gills for guiding the second fluid. By means of a so-called start-up flow forming on the gills, which has a high temperature gradient in a region of the corrugated fin, an improved heat transfer between the second fluid and the corrugated ribs is ensured.
Bevorzugt sind alle Kiemen eines zwischen zwei Flachrohren eingeschlossenen Rippenabschnitts einer Wellrippe in der gleichen Richtung gegenüber der Strömungsrichtung des zweiten Fluids schräg gestellt. Eine gleichartige Schrägstellung der Kiemen innerhalb eines Rippenabschnitts hat den Vorteil, daß damit gegebenenfalls die Strömung gezielt auf einen stromabwärts liegenden Rippenabschnitt lenkbar ist.Preferably, all the gills of a rib section enclosed between two flat tubes of a corrugated fin are inclined in the same direction with respect to the flow direction of the second fluid. A similar inclination of the gills within a rib section has the advantage that, if appropriate, the flow can be directed to a downstream rib section.
Die Kiemen versetzt hintereinander angeordneter Rippenabschnitte sind gegensinnig schräg gestellt, damit dem den Wärmetauscher durchströmenden zweiten Fluid ein längerer Strömungsweg vorgegeben wird. Die Kiemen zweier benachbarter Kiemenfelder können auch gleichsinnig schräg gestellt sein, wobei es dann unter Umständen vorteilhaft ist, wenn die Kiemen eines zu den beiden zueinander benachbarten Kiemenfeldern stromaufwärts beziehungsweise -abwärts angeordneten Kiemenfeldes gegensinnig zu den Kiemen der beiden zueinander benachbarten Kiemenfelder schräggestellt sind.The gills offset successively arranged rib portions are oppositely inclined, so that the heat exchanger through the flowing second fluid is given a longer flow path. The gills of two adjacent gill panels can also be placed obliquely in the same direction, it may then be advantageous if the gills of the two adjacent gill panels upstream or downstream gills are inclined in opposite directions to the gills of the two adjacent gill panels.
Eine gleichmäßige Abdeckung des vom zweiten Fluid durchströmten Strömungsquerschnitts wird bevorzugt dadurch erreicht, daß versetzt hintereinander angeordnete Rippenabschnitte parallel zueinander verlaufen. Hierbei stehen die zueinander versetzten Rippenabschnitte bevorzugt senkrecht auf den Flachrohren. Wenn die Rippenflächen etwas (bis etwa 6 Grad) von der Parallelität abweichen, wobei sie dann im Rahmen der Erfindung noch als im Wesentlichen parallel anzusehen sind, werden dadurch die thermodynamischen Vorteile der zueinander versetzten Rippen kaum beeinträchtigt. Ebenso ist die Verwendung von sogenannten V-Rippen oder auch von beliebig abgerundeten Rippen denkbar. Die erfindungsgemäße Rippengeometrie ist insbesondere bei Kraftfahrzeug-Wärmeübertragern wie Kühlmittelkühlern, Heizkörpern, Kondensatoren und Verdampfern anwendbar.Uniform coverage of the flow cross-section through which the second fluid flows is preferably achieved by displaced rib sections arranged one behind the other running parallel to one another. Here, the mutually offset rib sections are preferably perpendicular to the flat tubes. If the rib surfaces deviate slightly (up to about 6 degrees) from the parallelism, in which case they are still to be regarded as substantially parallel in the context of the invention, the thermodynamic advantages of the mutually offset ribs are scarcely impaired as a result. Likewise, the use of so-called V-ribs or even arbitrarily rounded ribs is conceivable. The rib geometry according to the invention is particularly applicable to automotive heat exchangers such as coolant radiators, radiators, condensers and evaporators.
Nach einer vorteilhaften Weiterbildung der Erfindung ist die Kiementiefe LP im Bereich von 0,7 bis 3 mm bei einem Kiemenwinkel von 20 bis 30 Grad leistungssteigernd, weil dadurch der Strömungswinkel, d.h. die Umlenkung des zweiten Fluids von einem Kanal in den benachbarten vergrößert wird, wodurch sich wiederum ein längerer Strömungsweg für das zweite Fluid ergibt. Die Rippenhöhe für ein solches System liegt vorteilhafterweise im Bereich von 4 bis 12 mm. Die Rippendichte für dieses System liegt vorteilhafterweise im Bereich von 40 bis 85 Ri/dm, was einem Rippenabstand bzw. einer Rippenteilung von 1,18 bis 2,5 mm entspricht.According to an advantageous development of the invention, the depth Kiement LP LP in the range of 0.7 to 3 mm at a gill angle of 20 to 30 degrees performance, because thereby the flow angle, i. the deflection of the second fluid is increased from one channel to the adjacent, which in turn results in a longer flow path for the second fluid. The rib height for such a system is advantageously in the range of 4 to 12 mm. The rib density for this system is advantageously in the range of 40 to 85 Ri / dm, which corresponds to a rib spacing or a rib pitch of 1.18 to 2.5 mm.
Ausführungsbeispiele werden nachfolgend anhand einer Zeichnung näher erläutert. Hierin zeigen:
- Fig. 1a,b
- einen Wärmetauscher mit zwei versetzt hintereinander angeordneten Wellrippen als Kühlrippen zwischen jeweils zwei benachbarten Flachrohren einer Rohrreihe,
- Fig. 2a,b
- einen Wärmetauscher mit drei versetzt hintereinander angeordneten Wellrippen als Kühlrippen zwischen jeweils zwei benachbarten Flachrohren einer Rohrreihe,
- Fig. 3
- zwei aus einem einzigen Band gebildete Wellrippen,
- Fig. 4
- drei aus einem einzigen Band gebildete Wellrippen,
- Fig. 5a
- eine Wellrippe ohne Versatz mit zwei Kiemenfeldern im Querschnitt,
- Fig. 5b
- eine Wellrippe ohne Versatz mit zwei Kiemenfeldern im Querschnitt,
- Fig. 5c
- eine Wellrippe aus einem
Band mit 2 Reihen im Querschnitt, - Fig. 5d
- eine Wellrippe aus einem
Band mit 3 Reihen im Querschnitt, - Fig. 5e
- eine Wellrippe aus einem
Band mit 4 Reihen im Querschnitt, - Fig. 5f
- eine Wellrippe aus einem
Band mit 5 Reihen im Querschnitt, - Fig. 5g
- eine Wellrippe aus einem
Band mit 5 Reihen im Querschnitt, - Fig. 5h
- eine Wellrippe aus einem
Band mit 5 Reihen im Querschnitt, - Fig. 5i
- eine Wellrippe aus einem
Band mit 3 Reihen im Querschnitt, - Fig. 5j
- eine Wellrippe aus einem
Band mit 3 Reihen im Querschnitt, - Fig. 5k
- eine Wellrippe aus einem
Band mit 3 Reihen im Querschnitt, - Fig. 5l
- eine Wellrippe aus einem
Band mit 5 Reihen im Querschnitt, - Fig. 6
- eine Momentaufnahme einer simulierten Luftströmung durch Wellrippen ohne Versatz,
- Fig. 7
- eine Momentaufnahme einer simulierten Luftströmung durch Wellrippen mit Versatz,
- Fig. 8
- eine Auftragung des Anteils eines durch eine Lamellenöffnung strömenden Luftmassenstroms an einem Gesamtluftmassenstrom gegen die Tiefe der Rohre bei geringer Luftanströmgeschwindigkeit,
- Fig. 9
- eine Auftragung des Anteils eines durch eine Lamellenöffnung strömenden Luftmassenstroms an einem Gesamtluftmassenstroms gegen die Tiefe der Rohre bei hoher Luftanströmgeschwindigkeit,
- Fig. 10a,b
- einen erfindungsgemäßen Wärmetauscher mit zwei versetzt hintereinander angeordneten Wellrippen als Kühlrippen zwischen jeweils zwei benachbarten Flachrohren zweier Rohrreihen, und
- Fig. 11 a,b
- einer erfindungsgemäßen Wärmetauscher mit drei versetzt hintereinander angeordneten Wellrippen als Kühlrippen zwischen jeweils zwei benachbarten Flachrohren zweier Rohrreihen.
- Fig. 1a, b
- a heat exchanger with two corrugated fins arranged behind one another as cooling fins between in each case two adjacent flat tubes of a row of tubes,
- Fig. 2a, b
- a heat exchanger with three corrugated fins arranged one behind the other as cooling fins between in each case two adjacent flat tubes of a row of tubes,
- Fig. 3
- two corrugated ribs formed from a single band,
- Fig. 4
- three corrugated ribs formed from a single band,
- Fig. 5a
- a corrugated rib without offset with two gill fields in cross section,
- Fig. 5b
- a corrugated rib without offset with two gill fields in cross section,
- Fig. 5c
- a corrugated rib of a band with 2 rows in cross section,
- Fig. 5d
- a corrugated rib from a band with 3 rows in cross-section,
- Fig. 5e
- a corrugated rib of a band with 4 rows in cross section,
- Fig. 5f
- a ribbed corrugated rib with 5 rows in cross section,
- Fig. 5g
- a ribbed corrugated rib with 5 rows in cross section,
- Fig. 5h
- a ribbed corrugated rib with 5 rows in cross section,
- Fig. 5i
- a corrugated rib from a band with 3 rows in cross-section,
- Fig. 5j
- a corrugated rib from a band with 3 rows in cross-section,
- Fig. 5k
- a corrugated rib from a band with 3 rows in cross-section,
- Fig. 5l
- a ribbed corrugated rib with 5 rows in cross section,
- Fig. 6
- a snapshot of a simulated air flow through corrugated ribs without offset,
- Fig. 7
- a snapshot of a simulated air flow through corrugated fins with offset,
- Fig. 8
- a plot of the proportion of air mass flow flowing through a louver opening to a total mass air flow against the depth of the tubes at a low air inflow velocity,
- Fig. 9
- a plot of the proportion of a mass air flow flowing through a fin opening in a total mass air flow against the depth of the tubes at high Luftanströmgeschwindigkeit,
- Fig. 10a, b
- a heat exchanger according to the invention with two successively arranged corrugated fins as cooling fins between each two adjacent flat tubes of two rows of tubes, and
- Fig. 11a, b
- a heat exchanger according to the invention with three successively arranged corrugated fins as cooling fins between each two adjacent flat tubes of two rows of tubes.
Einander entsprechende Teile sind in allen Figuren mit den gleichen Bezugszeichen versehen.Corresponding parts are provided in all figures with the same reference numerals.
Die
Zwischen zwei jeweils benachbarten Flachrohren 2 sind zwei (
Aus den Rippenabschnitten 4b heraus sind, wie insbesondere aus den
Zwei zwischen zwei Flachrohren 2 hintereinander angeordnete Wellrippen 3 sind um eine halbe Breite b zwischen benachbarten Rippenabschnitten 4b gegeneinander versetzt. Im Fall von drei hintereinander angeordneten Wellrippen 3, wie in den
Zwei bzw. drei benachbarte Wellrippen 3, die sich über die Tiefe T des Wärmetauschers 1 erstrecken, sind durch Walzen aus einem Band 8 erzeugt. Beim Walzen wird das Band 8 im Bereich des jeweiligen Versatzes zwischen den zwei (
Die an den Flachrohren 2 anliegenden Rippenabschnitte 4a der Wellrippen 3 weisen keine Kiemen auf. In diesem Bereich bildet sich daher eher eine laminare Strömung des Fluids FL2 aus als in den mit Kiemen 7 versehenen Rippenabschnitten 4b, die benachbarte Flachrohre 2 verbinden. Die laminare Strömung kann mit zunehmender Lauflänge zur Bildung einer Grenzschicht mit abnehmendem Temperaturgradienten am Flachrohr 2 führen. Dieser Effekt ist jedoch auf ein unbedeutendes Maß begrenzt, indem die sich zwischen zwei benachbarten Rippenabschnitten 4b einer Wellrippe 3 ausbildende Strömung des zweiten Fluids FL2 bereits nach der kurzen Wegstrecke T/2 (
Es können ferner zwei, drei oder auch mehr gleichartig geformte Wellrippen(Kühlrippen) versetzt zueinander hintereinander angeordnet sein, d.h. die eine Wellrippe mit strömungsleitenden Lamellen (Kiemen) kann in mehreren Ebenen versetzt zueinander liegen. Dabei kann die Anzahl der Wellrippen, die in Strömungsrichtung des zweiten Fluids betrachtet hintereinander angeordnet sind, in Abhängigkeit von der Tiefe des Wärmetauschers und/oder der Tiefe der Wellrippen gewählt werden. Dabei können bei einer Bautiefe von 12 bis 18 mm beispielsweise 2, 3 oder mehr Reihen Verwendung finden, bei einer Bautiefe bis 24 mm können beispielsweise 2, 3, 4 oder mehr Reihen Verwendung finden, bei einer Bautiefe bis 30 mm können beispielsweise 2, 3, 4, 5 oder mehr Reihen Verwendung finden, bei einer Bautiefe bis 36 mm können beispielsweise 2, 3, 4, 5, 6 oder mehr Reihen Verwendung finden, bei einer Bautiefe bis 42 mm können beispielsweise 2, 3, 4, 5, 6, 7 oder mehr Reihen Verwendung finden, bei einer Bautiefe bis 48 mm können beispielsweise 2, 3, 4, 5, 6, 7, 8 oder mehr Reihen Verwendung finden, bei einer Bautiefe bis 54 mm können beispielsweise 2, 3, 4, 5, 6, 7, 8, 9 oder mehr Reihen Verwendung finden, bei einer Bautiefe bis 60 mm können beispielsweise 2, 3, 4, 5, 6, 7, 8, 9, 10 oder mehr Reihen Verwendung finden, bei einer Bautiefe bis 66 mm können beispielsweise 2, 3, 4, 5, 6, 7, 8, 9, 10, 11 oder mehr Reihen Verwendung finden.It can also two, three or more similarly shaped corrugated fins (cooling fins) offset from each other to be arranged one behind the other, ie, the one corrugated fin with flow-conducting fins (gills) can be offset in several planes to each other. In this case, the number of corrugated fins, which are arranged one behind the other viewed in the direction of flow of the second fluid, depending on the depth of the heat exchanger and / or the depth of the corrugated fins are selected. For example, with a depth of 12 to 18 mm, 2, 3 or more rows can be used; for example, 2, 3, 4 or more rows can be used for a depth of up to 24 mm; for example, 2, 3 can be used for a depth of up to 30 mm , 4, 5 or more rows are used, with a construction depth of up to 36 mm, for example, 2, 3, 4, 5, 6 or more rows can be used, with a construction depth of up to 42 mm, for example, 2, 3, 4, 5, 6, 7 or more rows can be used, with a depth up to 48 mm, for example, 2, 3, 4, 5, 6, 7, 8 or more rows can be used, with a depth For example, 2, 3, 4, 5, 6, 7, 8, 9 or more rows can be used up to 54 mm, for example 2, 3, 4, 5, 6, 7, 8, 9, for a construction depth of up to 60 mm, 10 or more rows are used, with a depth up to 66 mm, for example, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11 or more rows can be used.
Ein Ausführungsbeispiel für 2 Reihen 15 und 16 zeigt
Ein Ausführungsbeispiel für 3 Reihen 17, 18 und 19 zeigt
Ein Ausführungsbeispiel für 4 Reihen 20, 21, 22 und 23 zeigt
Ein Ausführungsbeispiel für 5 Reihen 24, 25, 26, 27 und 28 zeigt
Ein Ausführungsbeispiel für 5 Reihen 29, 30, 31, 32 und 33 zeigt
Ein Ausführungsbeispiel für 5 Reihen 34, 35, 36, 37 und 38 zeigt
Mehr als zwei zueinander versetzte Reihen können vorzugsweise auf insgesamt zwei zueinander versetzte Ebenen verteilt sein wie bei den Ausführungsformen in den
Alternativ kann auch nur der Bereich 41 beziehungsweise 44 zwischen zwei in einer Ebene liegenden Kiemenfeldern 39, 40 beziehungsweise 42, 43 gegenüber den Kiemenfeldern 39, 40 beziehungsweise 42, 43 versetzt sein (
Ebenso können die Kiemenfelder 45, 46, 47 der Wellrippe 10k unterschiedlich groß sein (
Auch eine Kombination von verschiedengroßen Kiemenfeldern 65, 66, 67, 68, 69 in verschiedenen Ebenen ist wie bei der Wellrippe 10l möglich (
Die Anzahl der Kiemen pro Reihe liegt beispielsweise zwischen 2 und 30 Kiemen in Abhängigkeit der Anzahl der Reihen und der Tiefe des Wärmetauschers. Vorzugsweise ist die Anzahl der Kiemen pro Kiemenfeld aus fertigungstechnischen Gesichtspunkten bei ungerader Anzahl an Reihen, d.h. bei 3, 5, 7, 9 oder 11 Reihen nicht identisch. Bei gerader Anzahl an Reihen kann die Anzahl der Kiemen pro Kiemenfeld identisch sein, wobei dies nicht notwendig ist.The number of gills per row is for example between 2 and 30 gills depending on the number of rows and the depth of the heat exchanger. Preferably, the number of gills per gill field from an engineering point of view in odd number of rows, that is not identical at 3, 5, 7, 9 or 11 rows. With an even number of rows, the number of gills per gill panel can be identical, but this is not necessary.
Im folgenden (
Die Simulation erfolgt unter folgenden Bedingungen: Rohrwandtemperatur = 60 °C; Lufteintrittstemperatur = 45 °C; Luftdichte = 1,097 kg/m3; Lufteintrittsgeschwindigkeit vL = 1 und 3 m/s; Rippenhöhe = 8 mm; Rippentiefe = 16 mm. Bei der Simulation wird zum einen als Basis eine Wellrippe in einer Reihe, d.h. ohne Versatz, bestehend aus einer Reihe mit zwei Kiemenfeldern, die durch einen Steg in Dachform voneinander getrennt sind, betrachtet (Stand der Technik). Desweiteren wird eine Wellrippe mit 2 Reihen und eine Wellrippe mit 3 Reihen betrachtet. Die Simulation bestimmt neben dem luftseitigen Druckabfall den Massenstrom durch die einzelnen Lamellenöffnungen sowie die Abstrahlleistung von dem Rohr zur Kühlluft.The simulation takes place under the following conditions: pipe wall temperature = 60 ° C; Air inlet temperature = 45 ° C; Air density = 1.097 kg / m3; Air inlet velocity vL = 1 and 3 m / s; Rib height = 8 mm; Rib depth = 16 mm. In the simulation, on the one hand, a corrugated fin in a row, i. E. without offset, consisting of a row with two gill panels, which are separated by a ridge in the form of a roof, considered (prior art). Furthermore, a corrugated fin with 2 rows and a corrugated fin with 3 rows is considered. In addition to the air-side pressure drop, the simulation determines the mass flow through the individual fin openings as well as the radiation power from the pipe to the cooling air.
Wie aus
Wie aus
Die
Zwischen zwei jeweils benachbarten Flachrohren 2 sind zwei (
Aus den Rippenabschnitten 4b heraus sind Kiemen 7 geformt, die sich quer zur Strömungsrichtung S2 des zweiten Fluids FL2 sowie quer zur Strömungsrichtung S1 der ersten Fluide FL1a,b erstrecken. Die Kiemen 7 innerhalb eines Rippenabschnitts 4b bewirken zum einen eine besonders gute Wärmeübertragung zwischen dem zweiten Fluid FL2 und diesem Rippenabschnitt 4b, zum anderen eine gezielte Leitung des zweiten Fluids FL2 zum in Strömungsrichtung S2 schräg dahinter angeordneten Rippenabschnitt 4b. Auf diese Weise wird der den Wärmetauscher 1 durchströmende Massenstrom des zweiten Fluids FL2 praktisch vollständig unter hoher Ausnutzung des Temperaturunterschiedes zwischen den ersten Fluiden FL1a,b und dem zweiten Fluid FL2 zur Wärmeübertragung genutzt.
Zwei zwischen zwei Flachrohren 2 hintereinander angeordnete Wellrippen 3 sind gegeneinander versetzt. Die Herstellung dieser versetzten, einstückig ausgebildeten Wellrippen geschieht beispielsweise wie zu
In dem in den
Claims (9)
- Heat exchanger, in particular for motor vehicles, with flat tubes (2) through the inside of which first fluids (FL1a, FL1b) can flow and which can be exposed to a second fluid (FL2) on the outside, which are arranged substantially transversely to the flow direction (S2) of the second fluid (FL2) and parallel to one another in at least two rows, at least one tube row being assigned to each first fluid, such that the flat tubes of a tube row are spaced apart from one another and thereby form flow paths for the second fluid (FL2) flowing through the heat exchanger, and cooling fins are arranged in the said flow paths, which extend in each case between adjacent flat tubes (2), a plurality of corrugated fins (3) being provided as cooling fins arranged one behind another in the flow direction (S2) of the second fluid (FL2), the said fins being laterally offset relative to one another in an intermediate area (9) between the tube rows, and such that a plurality of corrugated fins (3) arranged one after the other are formed from a common strip (8), the corrugated fins (3) arranged one after another having gills (7) to deflect the second fluid (FL2),
characterised in that
the gills (7) of two fin sections (4b) arranged one behind the other and mutually offset are positioned obliquely in opposite directions. - Heat exchanger according to Claim 1,
characterised in that
The surfaces (5) of the corrugated fins (3) are arranged substantially parallel to the flow direction (S2) of the second fluid (FL2). - Heat exchanger according to Claims 1 or 2,
characterised in that
a plurality of corrugated fins (3) offset relative to one another are similarly shaped. - Heat exchanger according to any of the preceding claims,
characterised in that
all the gills (7) of a fin section (4b) bounded by two flat tubes (2) are angled obliquely in the same direction relative to the flow direction (S2) of the second fluid (FL2). - Heat exchanger according to any of Claims 1 to 4,
characterised in that
two mutually offset fin sections (4b) arranged one behind the other are substantially parallel to one another. - Heat exchanger according to Claim 5,
characterised in that
The fin sections (4b) are arranged substantially perpendicularly to the flat tubes (2). - Heat exchanger according to any of Claims 1 to 6,
characterised in that
the corrugated fins (3) extend for the same or a similar distance in the main flow direction of the second fluid. - Heat exchanger according to any of Claims 1 to 7,
characterised in that
different fluids flow through different tube rows. - Heat exchanger according to any of Claims 1 to 8,
characterised in that
one fluid flows through different tube rows.
Applications Claiming Priority (2)
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DE10342241A DE10342241A1 (en) | 2003-09-11 | 2003-09-11 | heat exchangers |
PCT/EP2004/008754 WO2005028987A1 (en) | 2003-09-11 | 2004-08-04 | Heat exchanger |
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EP (1) | EP1664655B1 (en) |
JP (1) | JP2007505282A (en) |
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FR2785978B1 (en) * | 1998-11-16 | 2001-03-30 | Valeo Thermique Moteur Sa | MULTIPLE HEAT EXCHANGER WITH COMMON INSERTS |
JP4122608B2 (en) * | 1998-12-10 | 2008-07-23 | 株式会社デンソー | Refrigerant evaporator |
JP4117429B2 (en) * | 1999-02-01 | 2008-07-16 | 株式会社デンソー | Heat exchanger fins |
FI109432B (en) * | 1999-03-16 | 2002-07-31 | Outokumpu Oy | Heat exchanger heat sink |
JP2001059690A (en) * | 1999-08-20 | 2001-03-06 | Zexel Valeo Climate Control Corp | Heat exchanger |
JP4207331B2 (en) * | 1999-09-29 | 2009-01-14 | 株式会社デンソー | Double heat exchanger |
US6401809B1 (en) * | 1999-12-10 | 2002-06-11 | Visteon Global Technologies, Inc. | Continuous combination fin for a heat exchanger |
US6729388B2 (en) * | 2000-01-28 | 2004-05-04 | Behr Gmbh & Co. | Charge air cooler, especially for motor vehicles |
EP1167909A3 (en) * | 2000-02-08 | 2005-10-12 | Calsonic Kansei Corporation | Core structure of integral heat-exchanger |
FR2807828B1 (en) * | 2000-04-17 | 2002-07-12 | Nordon Cryogenie Snc | CORRUGATED WING WITH PARTIAL OFFSET FOR PLATE HEAT EXCHANGER AND CORRESPONDING PLATE HEAT EXCHANGER |
DE10127084B4 (en) * | 2000-06-17 | 2019-05-29 | Mahle International Gmbh | Heat exchanger, in particular for motor vehicles |
US6435268B1 (en) * | 2001-05-10 | 2002-08-20 | Delphi Technologies, Inc. | Evaporator with improved condensate drainage |
DE50205000D1 (en) * | 2001-06-07 | 2005-12-29 | Behr Gmbh & Co Kg | Rib, pipe and heat exchanger |
US6805193B2 (en) * | 2002-01-24 | 2004-10-19 | Valeo, Inc. | Fin louver design for heat exchanger |
CN100354592C (en) * | 2002-03-09 | 2007-12-12 | 贝洱两合公司 | Heat exchanger |
DE10249451A1 (en) * | 2002-03-09 | 2003-09-18 | Behr Gmbh & Co | heat exchangers |
DE10218912A1 (en) * | 2002-04-27 | 2003-11-06 | Modine Mfg Co | Corrugated heat exchanger body |
KR20040017957A (en) * | 2002-08-23 | 2004-03-02 | 엘지전자 주식회사 | Exhauster for condensate of heat exchanger |
US6907919B2 (en) * | 2003-07-11 | 2005-06-21 | Visteon Global Technologies, Inc. | Heat exchanger louver fin |
-
2003
- 2003-09-11 DE DE10342241A patent/DE10342241A1/en not_active Withdrawn
-
2004
- 2004-08-04 US US10/571,295 patent/US20070267187A1/en not_active Abandoned
- 2004-08-04 JP JP2006525649A patent/JP2007505282A/en active Pending
- 2004-08-04 DE DE502004008363T patent/DE502004008363D1/en not_active Expired - Lifetime
- 2004-08-04 EP EP04763801A patent/EP1664655B1/en not_active Expired - Lifetime
- 2004-08-04 BR BRPI0414273-0A patent/BRPI0414273A/en not_active IP Right Cessation
- 2004-08-04 CN CNA2004800262193A patent/CN1849493A/en active Pending
- 2004-08-04 AT AT04763801T patent/ATE412865T1/en not_active IP Right Cessation
- 2004-08-04 WO PCT/EP2004/008754 patent/WO2005028987A1/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
US20070267187A1 (en) | 2007-11-22 |
BRPI0414273A (en) | 2006-11-07 |
EP1664655A1 (en) | 2006-06-07 |
ATE412865T1 (en) | 2008-11-15 |
DE502004008363D1 (en) | 2008-12-11 |
JP2007505282A (en) | 2007-03-08 |
DE10342241A1 (en) | 2005-04-07 |
CN1849493A (en) | 2006-10-18 |
WO2005028987A1 (en) | 2005-03-31 |
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