EP1527311B1 - Echangeur de chaleur a tuyaux plats - Google Patents

Echangeur de chaleur a tuyaux plats Download PDF

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Publication number
EP1527311B1
EP1527311B1 EP03766307.7A EP03766307A EP1527311B1 EP 1527311 B1 EP1527311 B1 EP 1527311B1 EP 03766307 A EP03766307 A EP 03766307A EP 1527311 B1 EP1527311 B1 EP 1527311B1
Authority
EP
European Patent Office
Prior art keywords
rib
heat exchanger
corrugated
radius
curvature
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03766307.7A
Other languages
German (de)
English (en)
Other versions
EP1527311A1 (fr
Inventor
Rainer Richter
Gerrit WÖLK
Ralf Bochert
Wolfgang Kramer
Martin Kaspar
Arnoldt Rehm
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Mahle Behr GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP1527311A1 publication Critical patent/EP1527311A1/fr
Application granted granted Critical
Publication of EP1527311B1 publication Critical patent/EP1527311B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F28D2021/0084—Condensers
    • 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
    • F28D2021/0091—Radiators
    • F28D2021/0094—Radiators for recooling the engine coolant

Definitions

  • the invention relates to a heat exchanger, in particular for motor vehicles, with a consisting of flat tubes and corrugated ribs, soldered heat transfer network according to the preamble of claim 1, known from the figure 6B US 6,308,527 B1 ,
  • the flat tubes of a liquid and / or vaporous medium eg. B. flows through a coolant or refrigerant, which dissipates its heat to the ambient air or absorbs heat from the ambient air.
  • a coolant or refrigerant which dissipates its heat to the ambient air or absorbs heat from the ambient air.
  • two very different heat capacity flows are in heat exchange with each other.
  • the surface of the corrugated fins is slotted, ie occupied with gills, which break up the forming boundary layer flows and a deflection of the air flow from one flow channel in the other and thus cause an extension of the flow path for the air.
  • the corrugated fins there are basically two different types, the so-called V-type with obliquely arranged to each other rib surfaces, known by the US-A 3,250,325 .
  • the second embodiment of the corrugated fin is the so-called U-type, in which the rib surfaces and thus also arranged on them gills are aligned parallel to each other-this U-type was by the US-A 5,271,458 known.
  • the U-type has some advantages over the V-type, namely a relatively uniform flow through the approximately rectangular rib channel, a uniform flow deflection through the gills, a higher air flow and thus a higher heat transfer performance.
  • the V-type is more advantageous because different rib densities can be produced with a constant rib bending radius for the wave comb by shirring or pulling apart the corrugated strip.
  • the rib radius or the rib distance is determined by the bending radius of the wave crest.
  • a disadvantage of the known parallel rib is further that the gill length is dependent on the rib bending radius, ie the larger the radius, the shorter the gill falls out, which has a performance-reducing effect.
  • the solution to this problem arises from the features of claim 1.
  • the known, formed by a constant curvature wave crest is inventively replaced by a bend, which is composed of three sections of different curvatures:
  • the middle section has a relatively small curvature, d. H. he is almost flat and thus is as far as possible on the outer surface of the pipe wall.
  • the radius of curvature of the elbow is larger in the central area than a rib height RH of the corrugated fin, more preferably 5 to 15 times the fin height RH.
  • a first outer portion has a radius of curvature R2 that is less than half the rib height RH of the corrugated fin, more preferably 3 to 20% of the fin height RH.
  • the radius of curvature R3 of the second outer portion of the elbow is greater than the radius of curvature R2 of the first outer portion.
  • This rib geometry in particular that of the elbow piece, can be produced relatively easily on conventional ribbed rollers.
  • the advantages of a parallel or rectangular rib are maintained, ie a relatively wide soldering surface with good heat transfer and optionally a large gill length, which extends almost over the entire rib height. If the rib surfaces deviate slightly (up to about 6 degrees) from parallelism, in which case they are still to be regarded as substantially parallel in the context of the invention, the thermodynamic advantages of the parallel rib are scarcely impaired as a result.
  • the rib geometry according to the invention is particularly applicable to automotive heat exchangers such asdekühlkühlem, radiators, condensers and evaporators.
  • the ribbed surfaces are occupied by gills, which preferably have a gage depth LP in a range of 0.5 to 1.5 mm, particularly advantageously in a range of 0.7 to 1.1 mm, with a gill angle between 20 and 35 degrees, particularly advantageous between 24 and 30 degrees.
  • gills have a performance-enhancing effect, because this improves the deflection of the air from one channel to the adjacent one, which in turn results in a longer flow path for the air.
  • the Kiementiefe in the range of 0.9 to 1.1 mm at a gill angle of 23 to 30 degrees is favorable for a pipe / rib system with a depth of 40 to 52 mm with a rib density of 45 to 65 ribs / dm, which corresponds to a rib distance of 1.538 to 2.222 mm.
  • the rib height for such a system is advantageously 7 to 9 mm.
  • Fig. 1 shows a so-called parallel rib 1, which extends between two flat tubes 2, 3 shown only partially.
  • the parallel or corrugated fin 1 and the flat tubes 2, 3 form a not shown brazed network of a heat exchanger, z. B. a coolant radiator for cooling an internal combustion engine of a motor vehicle or a condenser for a motor vehicle air conditioning.
  • the corrugated fin 1 has two mutually parallel, planar rib surfaces 4, 5, which are connected by a curved section 6.
  • the elbow 6 is in each case on the flat tubes 2, 3 and is soldered to them.
  • the flat rib surfaces 4, 5 are occupied by gills 7, which have a longitudinal extent LL.
  • the corrugated fin 1 has a fin height RH that is greater than the gill length LL.
  • the corrugated fin 1 has a certain rib density, which is characterized by the rib pitch, ie the dimension FP.
  • the elbow 6 is composed of three arc sections, namely a central portion 6a and two adjacent outer portions 6b, 6c. All three sections are formed by radii, the middle section having a relatively large radius R1 of about 50 to 70 mm.
  • the two outer radii R2 and R3 are considerably smaller, ie the radius R2 is in the range of 0, 4 to 0.6 mm, while the radius R3 is greater than the radius R2.
  • R3 is in the range of 0.6 to 1.1 or 1.3 mm.
  • This design of the elbow 6 results on the one hand a relatively wide soldering surface F, on the other hand a relatively large gill length LL, which is favorable for the heat transfer.
  • a parallel rib whose elbow 6 has the dimensions mentioned, can be easily manufactured on conventional ribbed rollers.
  • Fig. 2 shows a longitudinal section in the plane II-II, ie through the rib channel 8.
  • the rib surface 5 has a gill 9, which is composed of a plurality of individual gills 7.
  • the rib 5 has a rib depth RT, ie an extent in the air flow direction X.
  • Fig. 3 showed a section in the plane III-III in Fig.2
  • the gill field consists of front, in the drawing to the right rising gill 7a, a central roof-shaped Doppelkieme 7b and rear sloping right gill 7c.
  • the gills 7a, 7b, 7c are each inclined at a gill angle ⁇ .
  • the gills 7a, 7c have, measured in the air flow direction X, a dimension LP, which is referred to as the depth of the kite.
  • a dimension LP which is referred to as the depth of the kite.
  • a parallel rib system of the aforementioned dimensions is superior to a conventional rib system with a V-shaped rib in many respects, in terms of air flow, flow deflection, homogenization of flow velocity and temperature profile, and thus heat transfer performance.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (7)

  1. Echangeur de chaleur, en particulier radiateur à liquide de refroidissement ou condenseur pour véhicules automobiles, comprenant un réseau d'échangeurs de chaleur brasés se composant de tubes plats (2, 3) et d'ailettes ondulées (1), où les tubes plats (2, 3) sont traversés par un milieu liquide et / ou gazeux, les ailettes ondulées (1) étant baignées par de l'air, où une ailette ondulée (1) présente à chaque fois deux surfaces d'ailettes (4, 5) disposées pratiquement de façon parallèle l'une par rapport à l'autre, surfaces d'ailettes qui sont reliées par un raccord courbé (6) brasé avec un tube plat (2, 3), caractérisé en ce que le raccord courbé (6) présente, dans une partie médiane (6a), une courbure plus faible que celle dans une première partie extérieure (6b) et que celle dans une deuxième partie extérieure (6c), où le raccord courbé (6) présente, dans la partie médiane (6a), un rayon de courbure R1 qui est plus grand qu'une hauteur d'ailettes RH de l'ailette ondulée (1), et le raccord courbé (6) présente, dans la première partie extérieure (6b), un rayon de courbure R2 qui est plus petit qu'une moitié d'une hauteur d'ailettes RH de l'ailette ondulée (1), et le raccord courbé (6) présente, dans la deuxième partie extérieure (6c), un rayon de courbure R3 qui est plus grand qu'un rayon de courbure R2 dans la première partie extérieure (6b).
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les surfaces d'ailettes (4, 5) sont dotées d'ouïes (7).
  3. Echangeur de chaleur selon la revendication 2, caractérisé en ce que les ouïes (7, 7a, 7c) présentent une profondeur d'ouïes LP se situant dans une plage comprise entre 0,5 mm et 1,5 mm, et un angle d'ouïes α se situant dans la plage comprise entre 20° et 35°.
  4. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'ailette ondulée (1) présente une division d'ailettes FP se situant dans la plage comprise entre 1 mm et 3 mm.
  5. Echangeur de chaleur selon l'une quelconque des revendications 1 à 4, caractérisé en ce que l'ailette ondulée (1) présente une profondeur d'ailettes RT se situant dans la plage comprise entre 10 mm et 70 mm, de préférence entre 12 mm et 20 mm, ou bien entre 40 mm et 64 mm.
  6. Echangeur de chaleur selon l'une quelconque des revendications 2 à 5, caractérisé en ce que le rapport de la profondeur d'ouïes LP, sur la division d'ailettes FP, se situe dans une plage comprise entre 0,385 et 0,825.
  7. Echangeur de chaleur selon l'une quelconque des revendications 1 à 6, caractérisé en ce que l'ailette ondulée (1) présente une hauteur d'ailettes RH se situant dans une plage comprise entre 3 mm et 15 mm, de préférence entre 6 mm et 10 mm.
EP03766307.7A 2002-07-31 2003-07-25 Echangeur de chaleur a tuyaux plats Expired - Lifetime EP1527311B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10235038 2002-07-31
DE10235038A DE10235038A1 (de) 2002-07-31 2002-07-31 Flachrohr-Wärmeübertrager
PCT/EP2003/008251 WO2004013559A1 (fr) 2002-07-31 2003-07-25 Echangeur de chaleur a tuyaux plats

Publications (2)

Publication Number Publication Date
EP1527311A1 EP1527311A1 (fr) 2005-05-04
EP1527311B1 true EP1527311B1 (fr) 2016-05-04

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EP03766307.7A Expired - Lifetime EP1527311B1 (fr) 2002-07-31 2003-07-25 Echangeur de chaleur a tuyaux plats

Country Status (9)

Country Link
US (1) US7882708B2 (fr)
EP (1) EP1527311B1 (fr)
JP (1) JP2005534888A (fr)
CN (1) CN100373121C (fr)
AU (1) AU2003255295A1 (fr)
BR (1) BR0305705A (fr)
DE (1) DE10235038A1 (fr)
WO (1) WO2004013559A1 (fr)
ZA (1) ZA200409593B (fr)

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Also Published As

Publication number Publication date
CN100373121C (zh) 2008-03-05
DE10235038A1 (de) 2004-02-12
JP2005534888A (ja) 2005-11-17
AU2003255295A1 (en) 2004-02-23
US20050229630A1 (en) 2005-10-20
BR0305705A (pt) 2004-10-19
EP1527311A1 (fr) 2005-05-04
CN1672006A (zh) 2005-09-21
US7882708B2 (en) 2011-02-08
ZA200409593B (en) 2005-09-08
WO2004013559A1 (fr) 2004-02-12

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