EP2187157B1 - Echangeur de chaleur pour le chauffage d'un véhicule automobile - Google Patents

Echangeur de chaleur pour le chauffage d'un véhicule automobile Download PDF

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Publication number
EP2187157B1
EP2187157B1 EP09173650.4A EP09173650A EP2187157B1 EP 2187157 B1 EP2187157 B1 EP 2187157B1 EP 09173650 A EP09173650 A EP 09173650A EP 2187157 B1 EP2187157 B1 EP 2187157B1
Authority
EP
European Patent Office
Prior art keywords
flow
discs
deflection
disc
channels
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.)
Not-in-force
Application number
EP09173650.4A
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German (de)
English (en)
Other versions
EP2187157A2 (fr
EP2187157A3 (fr
Inventor
Michael Kohl
Thomas Strauss
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
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Filing date
Publication date
Application filed by Mahle Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP2187157A2 publication Critical patent/EP2187157A2/fr
Publication of EP2187157A3 publication Critical patent/EP2187157A3/fr
Application granted granted Critical
Publication of EP2187157B1 publication Critical patent/EP2187157B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F28D1/0341—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits

Definitions

  • the invention relates to a heat exchanger for heating a motor vehicle according to the preamble of claim 1.
  • Heat exchangers for heating motor vehicles are nowadays usually designed as soldered all-metal heat exchangers.
  • Known radiators have a radiator block, also called a short block, which is composed of tubes and ribs, preferably flat tubes and corrugated fins.
  • the pipes open into collection boxes and are soldered to the floors of the collection boxes.
  • the ribs of the block are overflowed by ambient air, which absorbs the heat of the coolant and transported into the passenger compartment.
  • An important criterion for a radiator is a uniform air outlet temperature distribution, if possible over the entire air outlet level, d. H. in height and in width direction.
  • FR 2 866 947 A1 discloses a device with combined heat exchangers.
  • the heat exchanger in short the radiator, is designed in disk construction, ie the flow channels are formed by a package of disks, one disk in each case has two interconnected disc halves, which are flowed through the heat transfer fluid, preferably a coolant Moflutig.
  • the disc design is known per se, especially in oil coolers for motor vehicles. Two disc halves each have an erect provided with a fold edge, which is integrally connected to the fold of the other disc, in particular by soldering.
  • the advantage of the disc construction is, inter alia, that the individual discs can be relatively easily added to a package and have geometrically simple, mostly flat solder surfaces, which can be soldered securely pressure and liquid-tight.
  • the manufacturing process of the disk-type radiator according to the invention is therefore easy to control, in particular no leaks are to be expected.
  • the discs have in their interior partitions to form flow channels, wherein deflecting zones are arranged at the end of the partition walls, so that adjacent flow channels are interconnected within a disc and the heat transfer fluid, in particular the coolant can be deflected in the depth direction.
  • the discs have inlet and outlet openings, which are cup-shaped and connected in a fluid-tight manner to the corresponding inlet and outlet openings of adjacent discs.
  • the inlet and outlet openings of a plurality of juxtaposed slices together form collecting channels which connect the slices to one another, ie the slices communicate on the coolant side via the collecting channels, both on the inlet and on the outlet side.
  • the collecting channels are thus comparable to the chambers of a collecting box, which is divided by a longitudinal partition wall.
  • the individual panes can be easily and safely soldered to each other via the cup-shaped openings, which each have peripheral folds.
  • the collecting ducts may be arranged on one side of the disk pack or on both sides, depending on where the inlet and / or outlet of the coolant is to be placed.
  • two adjacent collection channels are connected to one another by an outer deflection channel.
  • the deflection channel Through the deflection channel, the heat carrier fluid is led out of the disk package, mixed, introduced into the adjacent collection channel and distributed from there into the parallel flow channels of the individual disks.
  • an outer deflection channel Through this outer deflection, a homogenization of the air outlet temperature is achieved.
  • the flow cross section of the deflection channel is smaller than the sum of the flow cross sections of the flow channels in the discs.
  • the flow cross section of the deflection channel is preferably from 20 to 40% of the sum of the individual flow cross sections.
  • the radiator flows through four-flow, wherein the first and third deflection of the heat transfer fluid takes place within the discs and in the deflection zones, while the second deflection takes place outside the discs on the deflection channel.
  • the coolant temperature profile which is still asymmetrical after the first two flow passages is made uniform by the deflection of the coolant in the deflection channel, so that a homogeneous air outlet temperature profile results after the third and fourth passage of the coolant at the air outlet side.
  • the deflection channel is arranged within a first side part, which closes the disc package on one side to the outside.
  • a second side part which has an inlet and outlet opening and forms the end of the second side of the disk package to the outside.
  • the radiator according to the invention only three different items, d. H. three different types of discs.
  • the first type of disc has inlet and outlet openings, dividing walls and deflection zones.
  • the second disc type is formed as a first side part and has the deflection channel.
  • the third disc type is formed as a second side part and has an inlet and outlet opening.
  • secondary surfaces in particular corrugated fins are arranged between the discs, which increase the heat exchange surface on the air side, d. H. serve an improvement of the air side heat transfer.
  • Fig. 1 shows a radiator 1 according to the invention in disc design, ie the radiator 1 is constructed from a plurality of discs 2, which form flow channels for a heat transfer fluid, preferably for a coolant of a cooling circuit of an internal combustion engine of a motor vehicle.
  • the discs 2 have in their upper region cup-shaped openings 3, 4, 5, 6, which together with the adjacent cup-shaped openings, also called short wells 3, 4, 5, 6, collecting channels 7, 8, 9, 10 form.
  • the term "collection channel” which is used exclusively here also encompasses the term “distribution channel”.
  • the disks 2 do not have continuous partitions 11, 12 and a continuous partition wall 13 in the middle. All disks 2 are made of an aluminum material and soldered together, as will be explained in more detail later.
  • the flow path of the coolant is shown schematically by flow arrows K1 to K9.
  • the non-continuous partitions 11, 12 form deflection zones 14, 15, via which the coolant can be deflected in the depth direction.
  • the radiator 1 is traversed between the discs 2 of air, which is indicated by the two arrows L1, L2.
  • L1, L2 To improve the heat transfer 2 secondary surfaces, not shown, are arranged in the form of corrugated fins between the discs, which are soldered to the discs.
  • the heated air is - which is not shown - fed to the passenger compartment of a motor vehicle.
  • the coolant enters according to the arrow K1 in the collecting channel 7 of the radiator 1 and is distributed to the interiors of the individual panes 2 and flows in these according to the arrow K2 down.
  • the coolant is deflected in accordance with the arrow K3 in depth, ie opposite to the air flow direction L1, L2 and flows according to the arrow K4 upwards.
  • the arrows K2, K3, K4 apply to each individual slice 2 of the entire disc pack.
  • the coolant then collects in the collecting channel 8, from where it is led out according to the arrow K5 from the package of disks 2 via a channel, not shown here, and guided into the adjacent collecting channel 9.
  • Fig. 2 shows the radiator 1 in a perspective overall view with a first side part 16, in which a deflection channel 17 is formed.
  • the deflection channel 17 is above the two in Fig. 2 invisible cup openings 4, 5 with the collecting channels 8, 9 (see. Fig. 1 ) and thus causes the deflection of the coolant according to the arrow K5 in Fig. 1 , While the coolant according to the arrows K3, K7 is deflected within each of the individual disks 2, the deflection takes place according to the arrow K5 via the deflection channel 17 outside of the disks.
  • the flow cross section in the deflection channel 17 is preferably smaller than the sum of the flow channel cross sections of the individual disks 2, so that the coolant flow in the region of the deflection channel 17 undergoes a so-called throttling due to cross-sectional constriction. Due to the cross-sectional constriction creates a certain congestion effect, with the result that the emerging from the collecting channel 8 coolant is well mixed, ie receives a homogenized coolant temperature.
  • the flow cross section of the deflection channel 17 is preferably 20 to 40% of the sum of the flow channel cross sections in the individual disks 2. This measure of the "outer deflection" results in a largely homogeneous air temperature exit profile, ie on the side of the exiting air arrows L1, L2 (see. Fig. 1 ).
  • Fig. 3 shows the heating element 1 in a sectional view with flow arrows for the coolant and the air.
  • the entering coolant is indicated by an arrow K E and the escaping coolant by an arrow K A , while the entering into the radiator 1 air is marked L E.
  • the in the individual disks 2 perpendicular to the plane extending flow channels, corresponding to the arrows K2, K4, K6, K8 in Fig. 1 are in Fig. 3 marked as rows R1, R2, R3, R4.
  • the coolant flow thus runs in the row R1 according to the two arrow symbols (cross) down, in the row R2 corresponding to the arrow symbols (Point) up, in row R3 down and in row R4 back up.
  • each disc 2 consists of two disc halves 2a, 2b, each having a cup 3a, 3b, 4a, 4b, 5a, 5b, 6a, 6b.
  • Fig. 4 shows the radiator 1 in a plan view, wherein the discs 2, each consisting of the disc halves 2a, 2b, the first side member 16 with deflecting channel 17 and a second side member 18 are visible - they together form the disc package
  • Fig. 5 shows the second side part 18, which has an inlet opening 18a and an outlet opening 18b, which are arranged coaxially to the collecting channels 7 and 10.
  • the second disc part 18 thus acts as a connection part for the supply and discharge of the coolant.
  • Fig. 6 shows a single disc half 2a, with the two non-continuous partitions 11a, 12a and the continuous partition wall 13a.
  • the cups 3a, 4a, 5a, 6a are additionally arranged with arrow symbols for incoming and outgoing flow.
  • b4 could be twice that of b1.
  • the height of the deflection zones 14a, 15a is designated h1, where h1 ⁇ b1.
  • the height of the disk 2a is designated by h, where h According to a preferred embodiment in the range of 100 to 400 mm, while the construction or network depth T is in a range of 10 to 120 mm, preferably from 25 to 80 mm.
  • Fig. 7 shows a disc half 2a in a perspective "transparent" representation.
  • the non-continuous partition walls 11a, 12a and the continuous partition wall 13a are raised in the form of embossed beads.
  • Fig. 8 shows a disc 2, made up of two disc halves 2a, 2b, in perspective "transparent" representation. Both disc halves 2a, 2b are soldered together over the entire circumference, via the partitions 11a, 12a, 13a tightly together.
  • Fig. 9 shows a half disc 2a in section, wherein the formed as trapezoidal beads partitions 11a, 12a, 13a are visible.
  • Fig. 10 shows the disc 2, consisting of the disc halves 2a, 2b, in section.
  • the disc 2 has a circumferential, soldered fold 19 and is thus sealed to the outside.
  • the partitions 11, 12, 13 are formed to form the flow channels.
  • Fig. 10a shows a detail E from Fig. 10 in an enlarged view, in which a channel width B1 (clear width), a cup height B3 and a material thickness s are shown.
  • the channel width B1 is preferably selected in a range of 0.5 to 2.5 mm, and the cup height B3 ranges in the range of 1.5 to 5.0 mm. This measure corresponds to half the width of a corrugated fin, which is arranged between the discs 2.
  • the material thickness s ranges from 0.15 to 0.5 mm for an aluminum material.
  • Fig. 11 shows a section through the disc 2 in the region of the wells 3, 4, 5, 6, which determine the maximum height of the disc 2, marked B4.
  • B4 is preferably in the range of 3.8 to 13.5 mm.
  • the entire radiator 1 can be made according to the illustrated and described embodiment of only three different items: these are the disc 2, consisting of two disc halves 2a, 2b, the first side member 16 with deflection 17 and the second side member 18 with inlet and outlet openings 18a, 18b.
  • the small number of individual parts lowers the manufacturing costs.
  • the soldering process is easy to control because all the surfaces to be soldered are even (circumferential fold, partitions, cups), so that an error-free Dichtlötung is guaranteed. With this design, a radiator with multiple deflection can thus be produced process reliable.
  • turbulence sheets can be arranged in the disks 2, which are also soldered to the disks.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)

Claims (6)

  1. Radiateur de chauffage (1) servant au chauffage d'un véhicule automobile, ledit radiateur de chauffage présentant une multiplicité de conduits d'écoulement qui, côté primaire, sont traversés par un fluide d'échangeur de chaleur, et qui, côté secondaire, sont baignés par de l'air, où le flux de fluide de l'échangeur de chaleur et le flux d'air sont guidés dans le flux opposé croisé, et le flux de fluide de l'échangeur de chaleur circulant dans le sens opposé à la direction d'écoulement de l'air est redirigé au moins deux fois, où les conduits d'écoulement sont formés par un paquet de plaques (2), où une plaque (2) présente deux moitiés de plaque (2a, 2b) et peut être traversée par au moins trois flux, où des parois de séparation (11, 12, 13) servant à la configuration des conduits d'écoulement sont disposées dans les plaques (2), et des zones de retour de flux (14, 15) sont formées au niveau de l'extrémité des parois de séparation (11, 12), zones de retour de flux qui relient des conduits d'écoulement adjacents, où les plaques (2) présentent des ouvertures d'entrée et de sortie (3, 4, 5, 6) configurées en forme de godet, ouvertures d'entrée et de sortie qui communiquent, de façon étanche aux fluides, avec les ouvertures d'entrée et de sortie (3, 4, 5, 6) de plaques adjacentes (2), où chaque plaque (2) présente deux ouvertures d'entrée (3, 5) et deux ouvertures de sortie (4, 6), où les ouvertures d'entrée et de sortie (3, 4, 5, 6), en forme de godet, forment des conduits collecteurs (7, 8, 9, 10), où deux conduits collecteurs adjacents (8, 9) sont reliés l'un à l'autre par un conduit extérieur de retour de flux (17), et où il se produit, à l'intérieur des plaques (2) et dans les zones de retour de flux (14, 15), un premier et un troisième retour de flux (K3, K7) du fluide de l'échangeur de chaleur, et il se produit, à l'extérieur des plaques (2) via le conduit de retour de flux (17), un deuxième retour de flux (K5), où le conduit de retour de flux (17) est disposé à l'intérieur d'une première partie latérale (16) qui ferme, vers l'extérieur, le paquet de plaques, caractérisé en ce que le radiateur de chauffage (1) présente une seconde partie latérale (18) qui présente des ouvertures d'entrée et de sortie (18a, 18b).
  2. Radiateur de chauffage selon la revendication 1, caractérisé en ce que les ouvertures d'entrée et de sortie (3, 4, 5, 6), respectivement les conduits collecteurs (7, 8, 9, 10), sont disposé (e) s sur un côté ou sur les deux côtés des plaques (2).
  3. Radiateur de chauffage selon la revendication 1 ou 2, caractérisé en ce que la section d'écoulement du conduit de retour de flux (17) est inférieure à la somme des sections d'écoulement des conduits d'écoulement formés dans les plaques (2), et est comprise, de préférence, entre 20 % et 40 % de la somme des sections d'écoulement.
  4. Radiateur de chauffage selon l'une quelconque des revendications précédentes, caractérisé en ce que le radiateur de chauffage est constitué de trois pièces détachées différentes (2, 16, 18).
  5. Radiateur de chauffage selon l'une quelconque des revendications précédentes, caractérisé en ce que des surfaces secondaires, en particulier des ailettes ondulées, sont disposées entre les plaques (2).
  6. Radiateur de chauffage selon l'une quelconque des revendications précédentes, caractérisé en ce que des tôles générant des turbulences sont disposées à l'intérieur des plaques (2).
EP09173650.4A 2008-11-18 2009-10-21 Echangeur de chaleur pour le chauffage d'un véhicule automobile Not-in-force EP2187157B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200810058100 DE102008058100A1 (de) 2008-11-18 2008-11-18 Wärmeübertrager zur Beheizung eines Kraftfahrzeugs

Publications (3)

Publication Number Publication Date
EP2187157A2 EP2187157A2 (fr) 2010-05-19
EP2187157A3 EP2187157A3 (fr) 2013-10-16
EP2187157B1 true EP2187157B1 (fr) 2019-03-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP09173650.4A Not-in-force EP2187157B1 (fr) 2008-11-18 2009-10-21 Echangeur de chaleur pour le chauffage d'un véhicule automobile

Country Status (3)

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EP (1) EP2187157B1 (fr)
CN (1) CN101738100A (fr)
DE (1) DE102008058100A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2993354B1 (fr) * 2012-07-13 2018-07-13 Delphi Automotive Systems Lux Refroidisseur d'air de suralimentation
CN105806097A (zh) * 2014-12-30 2016-07-27 重庆联合机器制造有限公司 多通道多流程空气冷却器及其制备方法
CN107228582A (zh) * 2016-03-25 2017-10-03 丹佛斯微通道换热器（嘉兴）有限公司 板式换热器
CN107664445A (zh) * 2016-07-28 2018-02-06 恒丰工程（香港）有限公司 多流程可拆卸板式换热器及其专用换热板
FR3068118A1 (fr) * 2017-06-22 2018-12-28 Valeo Systemes Thermiques Evaporateur, notamment pour circuit de climatisation de vehicule automobile, et circuit de climatisation correspondant
CN114234699A (zh) * 2021-12-13 2022-03-25 浙江银轮新能源热管理系统有限公司 芯片单元、芯体及冷却器

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JPS6213998A (ja) * 1985-07-10 1987-01-22 Sakae Sangyo Kk パネル型熱交換器
US20010018968A1 (en) * 2000-03-02 2001-09-06 Behr Gmbh & Co. Heat exchanger and heating or air conditioning unit of a motor vehicle containing said heat exchanger
EP1247666A1 (fr) * 2001-04-06 2002-10-09 Behr GmbH & Co. Echangeur de chaleur et appareil de chauffage ou climatisation de voiture comprenant un tel échangeur de chaleur
FR2866947A1 (fr) * 2004-02-27 2005-09-02 Valeo Climatisation Dispositif a echangeurs de chaleur combines

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JPH03140795A (ja) * 1989-10-25 1991-06-14 Hitachi Ltd 積層形熱交換器
JP2917764B2 (ja) * 1992-09-17 1999-07-12 株式会社デンソー 冷房装置用蒸発器
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DE9400502U1 (de) * 1994-01-13 1994-02-24 Behr Gmbh & Co, 70469 Stuttgart Wärmetauscher, insbesondere Kältemittelverdampfer
US5678419A (en) * 1994-07-05 1997-10-21 Nippondenso Co., Ltd Evaporator for a refrigerating system
DE4431192C1 (de) * 1994-09-01 1996-02-29 Himmelsbach Johann Verfahren zur Beheizung der Kabine von Kraftfahrzeugen mit der Abwärme des Antriebsmotors
US5860595A (en) 1994-09-01 1999-01-19 Himmelsbach; Johann Motor vehicle heat exhanger
FR2728665A1 (fr) * 1994-12-26 1996-06-28 Valeo Thermique Habitacle Echangeur de chaleur a trois fluides de construction simplifiee
DE19752139B4 (de) 1997-11-25 2004-06-03 Behr Gmbh & Co. Wärmeübertrager für ein Kraftfahrzeug
EP1360445B1 (fr) * 2001-02-05 2007-08-29 Showa Denko K.K. Echangeur thermique de type duplex et systeme de refrigeration equipe de cet echangeur
FR2861166B1 (fr) * 2003-10-21 2006-11-24 Valeo Climatisation Echangeur de chaleur utilisant un fluide d'accumulation
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Publication number Priority date Publication date Assignee Title
JPS6213998A (ja) * 1985-07-10 1987-01-22 Sakae Sangyo Kk パネル型熱交換器
US20010018968A1 (en) * 2000-03-02 2001-09-06 Behr Gmbh & Co. Heat exchanger and heating or air conditioning unit of a motor vehicle containing said heat exchanger
EP1247666A1 (fr) * 2001-04-06 2002-10-09 Behr GmbH & Co. Echangeur de chaleur et appareil de chauffage ou climatisation de voiture comprenant un tel échangeur de chaleur
FR2866947A1 (fr) * 2004-02-27 2005-09-02 Valeo Climatisation Dispositif a echangeurs de chaleur combines

Also Published As

Publication number Publication date
EP2187157A2 (fr) 2010-05-19
DE102008058100A1 (de) 2010-05-20
EP2187157A3 (fr) 2013-10-16
CN101738100A (zh) 2010-06-16

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