EP2622299A2 - Échangeur de chaleur - Google Patents

Échangeur de chaleur

Info

Publication number
EP2622299A2
EP2622299A2 EP11757177.8A EP11757177A EP2622299A2 EP 2622299 A2 EP2622299 A2 EP 2622299A2 EP 11757177 A EP11757177 A EP 11757177A EP 2622299 A2 EP2622299 A2 EP 2622299A2
Authority
EP
European Patent Office
Prior art keywords
planar wall
heat exchanger
wall portions
plates
recess
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP11757177.8A
Other languages
German (de)
English (en)
Other versions
EP2622299B1 (fr
Inventor
Heinrich J Kuehne
Thomas Cott
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.)
Hydac Cooling GmbH
Original Assignee
Hydac Cooling GmbH
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 Hydac Cooling GmbH filed Critical Hydac Cooling GmbH
Publication of EP2622299A2 publication Critical patent/EP2622299A2/fr
Application granted granted Critical
Publication of EP2622299B1 publication Critical patent/EP2622299B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements

Definitions

  • the invention relates to a heat exchanger, in particular for Fluidkühlvor- directions, with a package of plane-parallel plates, between pairs of superimposed plates in alternation fürström Kunststoffe for a hot medium and a cooling medium are formed, which are laterally bounded by the plates at a distance holding profile strips which form soldering surfaces adjacent to the plates, the profiled strips extending along the flow-through regions of one medium and the other medium along edges of the plates which are at an angle to one another and wherein at least the profiled strips of the flow-through regions of the cooling medium comprise a main body, two extending from it The limbs extending limbs and between these have an open to the adjacent flow area recess.
  • Heat exchangers of this type are state of the art, cf. DE 20 208 748 U1.
  • air as the cooling medium
  • heat exchangers are often used for cooling hydraulic fluids for the working hydraulics of mechanical systems, such as construction machinery.
  • the heat exchangers are exposed not only to mechanical loads, but also to thermal loads due to the high operating temperature of the fluids to be cooled. This is especially the Fall, when intermittent operations, temperature jumps result, which leads due to material strains to strong voltages in the package of components that are connected by soldering to form a rigid block. The result is stress cracks, especially in the area of the solder joints, with the risk of failure of the heat exchanger and thus the threat to the associated system.
  • the invention has for its object to provide a heat exchanger available, which is characterized by an improved resistance to operating loads, so that a safe long-term operation is possible.
  • a significant feature of the invention is that the shape of the adjacent to the solder surfaces of the leg cross-section is optimized in terms of avoiding excessive stresses by special shaping of the recess at least in the adjacent to the cooling medium profile strips , Due to the fact that the recess, starting from the inner end portion, has planar wall parts, an at least approximately linear change of the flexural strength over the length of the profile legs can be achieved, so that by selecting the length and / or the inclination of these planar wall parts relative to the surface of the soldering surface an optimal bending behavior of the legs is achievable.
  • the arrangement may in this case be such that the recess, starting from its inner end portion, diverging first planar wall parts, which become narrow points of the
  • Cross-section of the legs extend to join the bottlenecks- de, converging second planar wall parts and adjoining third planar wall parts which, parallel to the soldering surfaces, extend in the vicinity of the opening of the recess.
  • zones of lower flexural strength are formed on the profile limbs, adjoining leg sections on both sides in which the bending resistance increases substantially linearly.
  • the bottlenecks not only define a bending line of a kind of bending joint, but also represent the location of the steepest temperature gradient. Since this is effective at the location of the smallest material cross section, correspondingly low material expansions and stresses result.
  • the recess is shaped in such a way that adjoin the third planar wall parts fourth planar wall parts which extend slightly divergent to the opening of the recess to each other.
  • the first planar wall portions may form mutually perpendicular planes, and the second planar wall portions may include an obtuse angle with the first planar wall portions, which is preferably only slightly larger than a right angle.
  • the cross-sectional shape of the recess in the region adjacent to the inner end corresponds approximately to a square open towards the opening.
  • the arrangement can be made such that the first planar wall parts are connected to each other and these with the second planar wall parts each over curved wall locations with the same radius of curvature.
  • the second planar wall parts are preferably also provided with the third planar wall parts and those with the fourth planar wall parts also each with arched wall locations connected to the same, the second radius of curvature, which is twice the first radius of curvature.
  • the arrangement is preferably such that the thickness of the cross section of the legs in the region of the third planar wall parts is approximately twice the thickness of the cross section at the bottlenecks is.
  • perspective oblique view ledigl I a corner region of a portion of the plate pack of an embodiment of the heat exchanger according to the invention and an enlarged drawn side view only a profile bar to form a spacer between plates of the package.
  • FIG. 1 illustrates an exemplary embodiment in the form of a conventional plate-type heat exchanger with a stack of flat plates 1, preferably made of an aluminum alloy, which run in parallel planes and form separating plates for flow areas located between them, wherein between successive pairs of plates in alternation in each case a flow area 3 for the medium to be cooled, for example, hydraulic oil, and a flow area 5 for a cooling medium, such as cooling air, are formed.
  • a flow area 3 for the medium to be cooled for example, hydraulic oil
  • a flow area 5 for a cooling medium such as cooling air
  • the flow area 3 for the hot medium lying above in the drawing is closed on two opposite sides by conventionally shaped end strips 7, between which the respective inflow and outflow areas are located, turbulators 9 being connected between the end strips 7 in the usual way are provided in the form of slats.
  • the flow area 5 of the cooling medium is laterally also bounded by end strips, which form the spacers between the respective plate pair and which are formed as a professional Most 1 1 with special, inventive design.
  • This embodiment of the invention is explained in more detail with reference to FIG.
  • the profile strips 1 1 which are also preferably extruded from an aluminum alloy, have a cuboid or block-shaped basic body 1 3 facing the edge region of the plates 1, a recess 15 in the form of a continuous longitudinal groove and the recess 15 limbs bounding on both sides 1 7 on.
  • the recess 15 is open to the flow-through region 5, in which cooling fins 19 are located, which, just like the turbulators 9 in the flow-through region 3, increase the effective heat transfer area.
  • the inner end portion 23 ( Figure 2) of the recess 1 5 is located from the closed end 21 of the profile strip 1 1 at a distance which is slightly greater than the distance between the end portion 23 and opening of the recess 15.
  • the lips 27 support the lamellae 5 in front of the end of the soldering surfaces 25, so that when stacking the risk is avoided that lamella ends penetrate into the gap between the plate 1 and solder 25.
  • the recess 1 starting from its inner end portion 23, bounded by planar wall portions 29 which, diverging to each other and enclosing a right angle, extend into the vicinity of the respective soldering surface 25 and there a Profilengstelle 31 of the profile cross section of the legs 1 7 form.
  • the constriction 31 is adjoined by second planar wall parts 33, which converge in a convergent manner and enclose an obtuse angle with the first planar wall parts 29, which angle is slightly larger than a right angle.
  • the length of these second planar wall portions 33 is slightly smaller than the length of the first planar wall portions 29, and these third planar wall portions 33 are followed by third planar wall portions 35 defining planes parallel to the soldering surfaces 25 and extending into the vicinity of the opening the recess 15 extend. At this third planar wall portions 35 in turn close fourth planar wall portions 37 which extend slightly divergent to the opening of the recess 15 to each other.
  • the connection of the first planar wall portions 29 with each other and with the second planar wall portions 33 takes place in each case via curved wall portions 39 with the same radius of curvature.
  • the connection of the second planar wall portions 33 with the third planar wall portions 35 and this with the fourth planar wall portions 37 also takes place over curved wall portions 41, in which the radius of curvature is twice the radius of curvature at the wall portions 39.
  • the inventively provided cross-sectional shape of the recess 1 5 results in an effective reduction of operational voltage peaks and the risk of cracking at the solder joints.
  • the bottlenecks 31st on the thigh profile the location of the steepest temperature gradient.
  • this is also the location of the smallest material cross-section, so that thermal deformations are limited to correspondingly limited material parts. Since the profile thickness of the legs 1 7, starting from the constrictions 31, increases towards the opening to a profile thickness which corresponds approximately to twice the constrictions 31, an optimum stress distribution over the area of the soldering surfaces 25 results.
  • the heat exchanger device according to the invention need not be limited to the field of fluid cooling, but can also be used generally for the cooling of gaseous media and here in particular intercooler (diesel engines), as well as secondary and intercooler (compressors) to include.
  • intercooler diesel engines
  • secondary and intercooler compressors
  • the temperature differences (cooling air to medium) in the pertinent applications are comparatively much higher than described above.

Landscapes

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

Abstract

L'invention concerne un échangeur de chaleur, notamment pour des dispositifs de refroidissement de liquides, comprenant un ensemble de plaques à faces planes et parallèles (1), des zones de passage (3, 5) pour un milieu chaud et pour un milieu de refroidissement étant formées en alternance entre des paires de plaques superposées (1), lesdites zones de passage étant délimitées latéralement par des baguettes profilées (7, 11) qui maintiennent les plaques (1) à distance, forment des surfaces de brasage (25) en contact avec les plaques (1) et s'étendent, au niveau des zones de passage (3, 5) desdits milieux, le long de bords contigus des plaques, à angle droit, au moins les baguettes profilées (11) des zones de passage (5) du milieu de refroidissement présentant un corps de base (13), deux branches (17) s'étendant à partir de ce dernier le long des surface de brasage (25) ainsi que, entre les deux branches, un évidement (15) ouvert en direction de la zone de passage (5) adjacente. Cet échangeur de chaleur est caractérisé en ce que l'évidement (15) est délimité, au moins dans la zone adjacente à sa partie d'extrémité intérieure (23), par des parties de parois à surfaces planes (29).
EP11757177.8A 2010-09-29 2011-09-09 Échangeur de chaleur Not-in-force EP2622299B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010046913A DE102010046913A1 (de) 2010-09-29 2010-09-29 Wärmetauscher
US12/923,905 US8579021B2 (en) 2010-09-29 2010-10-13 Heat exchanger
PCT/EP2011/004545 WO2012052093A2 (fr) 2010-09-29 2011-09-09 Échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP2622299A2 true EP2622299A2 (fr) 2013-08-07
EP2622299B1 EP2622299B1 (fr) 2017-04-12

Family

ID=44651638

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11757177.8A Not-in-force EP2622299B1 (fr) 2010-09-29 2011-09-09 Échangeur de chaleur

Country Status (5)

Country Link
US (1) US8579021B2 (fr)
EP (1) EP2622299B1 (fr)
CN (1) CN103097848B (fr)
DE (1) DE102010046913A1 (fr)
WO (1) WO2012052093A2 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202011052186U1 (de) * 2011-12-05 2013-03-06 Autokühler GmbH & Co KG Wärmeaustauscher
DE102014001703A1 (de) 2014-02-08 2015-08-13 Hydac Cooling Gmbh Wärmetauschvorrichtung
WO2017059952A1 (fr) * 2015-10-06 2017-04-13 Linde Aktiengesellschaft Profilés de bordure munis d'une structure de surface pour échangeur de chaleur à plaques
EP3473961B1 (fr) 2017-10-20 2020-12-02 Api Heat Transfer, Inc. Échangeur de chaleur
US10465992B2 (en) * 2018-03-16 2019-11-05 Hamilton Sundstrand Corporation Parting sheet in heat exchanger core
US11168943B2 (en) 2018-10-12 2021-11-09 Api Heat Transfer Thermasys Corporation Channel fin heat exchangers and methods of manufacturing the same
WO2020160800A1 (fr) 2019-02-07 2020-08-13 Hydac Cooling Gmbh Échangeur de chaleur
US11221186B2 (en) * 2019-07-18 2022-01-11 Hamilton Sundstrand Corporation Heat exchanger closure bar with shield
DE102020001455A1 (de) 2020-03-06 2021-09-09 Hydac Ag Wärmetauscher

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK48245C (da) * 1930-07-26 1934-01-08 Curt Fredrik Rosenblad Anordning ved Varmeudvekslingsapparater til Vædsker med Varmeoverføringsflader bestaaende af spiralformet sammenrullede Plader.
US3252510A (en) * 1964-08-14 1966-05-24 Stewart Warner Corp Heat exchanger using brazed joints
US3601185A (en) * 1969-11-04 1971-08-24 United Aircraft Corp Heat exchanger construction
DE3521914A1 (de) 1984-06-20 1986-01-02 Showa Aluminum Corp., Sakai, Osaka Waermetauscher in fluegelplattenbauweise
EP0203458B1 (fr) 1985-05-15 1988-08-24 Showa Aluminum Corporation Echangeur de chaleur à plaques et à ailettes
US4681155A (en) * 1986-05-01 1987-07-21 The Garrett Corporation Lightweight, compact heat exchanger
JPH0539323Y2 (fr) * 1987-05-29 1993-10-05
DE19651625A1 (de) * 1996-12-12 1998-06-18 Behr Industrietech Gmbh & Co Wärmeübertrager
US6520252B1 (en) * 2001-12-21 2003-02-18 Hamilton Sundstrand Heat exchanger assembly with core-reinforcing closure bars
DE20208748U1 (de) 2002-05-31 2003-10-02 Autokuehler Gmbh & Co Kg Wärmeaustauschernetz, insbesondere für Hochtemperaturanwendungen
DE10347677A1 (de) * 2003-10-09 2005-05-04 Behr Industrietech Gmbh & Co Kühlerblock, insbesondere für einen Ladeluft/Kühlmittel-Kühler
US8276654B2 (en) * 2005-11-17 2012-10-02 Hamilton Sundstrand Corporation Core assembly with deformation preventing features
CN201110683Y (zh) * 2007-10-18 2008-09-03 重庆大学 一种板翅式冰蓄冷器
DE202008013351U1 (de) 2008-10-08 2010-03-25 Autokühler GmbH & Co. KG Wärmeaustauschernetz und damit ausgerüsteter Wärmeaustauscher

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012052093A2 *

Also Published As

Publication number Publication date
US20120073793A1 (en) 2012-03-29
EP2622299B1 (fr) 2017-04-12
CN103097848A (zh) 2013-05-08
WO2012052093A2 (fr) 2012-04-26
CN103097848B (zh) 2015-07-29
US8579021B2 (en) 2013-11-12
DE102010046913A1 (de) 2012-03-29
WO2012052093A3 (fr) 2012-08-23

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