EP1962041A2 - Dispositif d'échange de chaleur - Google Patents

Dispositif d'échange de chaleur Download PDF

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Publication number
EP1962041A2
EP1962041A2 EP08100462A EP08100462A EP1962041A2 EP 1962041 A2 EP1962041 A2 EP 1962041A2 EP 08100462 A EP08100462 A EP 08100462A EP 08100462 A EP08100462 A EP 08100462A EP 1962041 A2 EP1962041 A2 EP 1962041A2
Authority
EP
European Patent Office
Prior art keywords
channel
flow
ribs
heat transfer
cooling fluid
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.)
Withdrawn
Application number
EP08100462A
Other languages
German (de)
English (en)
Other versions
EP1962041A3 (fr
Inventor
Hans-Ulrich Kühnel
Dieter Thönnessen
Michael Sanders
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.)
Pierburg GmbH
Original Assignee
Pierburg 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 Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP1962041A2 publication Critical patent/EP1962041A2/fr
Publication of EP1962041A3 publication Critical patent/EP1962041A3/fr
Withdrawn legal-status Critical Current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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
    • 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
    • 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
    • F28D9/0025—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 being formed by zig-zag bend plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/06—Hollow fins; fins with internal circuits

Definitions

  • the invention relates to a heat transfer device, which is composed of a plurality of housing parts, which are interconnected such that at least one of a fluid to be cooled flowed through the channel and at least one of a cooling fluid flow-through channel in heat exchanging contact with each other are arranged, of at least one the housing parts extend ribs in the flow-through of the fluid to be cooled channel.
  • Such heat exchangers are used for example as a cooler in internal combustion engines.
  • applications for cooling the exhaust gas and for cooling the charge air are known. In both cases, this cooling is used to improve the combustion process and thus reduce the pollution of the exhaust gas with pollutants.
  • heat exchangers and here in particular made of die-cast heat exchanger from a plurality of nested shells, from which extend ribs, in particular in the flowed through by the fluid to be cooled channel.
  • this case usually serves the base plate, from which extend the ribs, as a partition between the coolant channel and the gas usually leading channel.
  • Such a heat transfer device is for example from the DE 20 2006 009 464 U1 known.
  • This heat exchanger has an internal coolant channel, from which ribs extend into a channel through which exhaust gas flows, for example.
  • the ribs have a main flow direction the exhaust gas of elongated shape, are arranged offset to one another in the flow direction and formed interrupted transversely to the flow direction.
  • this heat exchanger already has a good cooling efficiency due to its rib shape, it remains desirable to additionally increase it or to reduce the necessary installation space while maintaining the same cooling capacity.
  • the ribs in the interior have a through-flow of the cooling fluid cavity which extends from the cooling fluid flow-through channel into the rib.
  • the fin efficiency is improved because the distance between the coolant and gas leading channel is reduced.
  • the rib itself reaches a lower temperature over its height, so that the temperature difference with the exhaust gas increases, as a result of which the heat exchange between the rib and the exhaust gas is improved.
  • the cavity extends substantially over the entire height of the rib, so that even in areas where usually the cooling effect of the rib decreases considerably due to a higher existing temperature, the temperature can be significantly reduced and thus the fin efficiency over the entire channel height of the channel through which the fluid to be cooled can be improved.
  • guide devices for forced flow through the ribs are arranged in the channel through which the cooling fluid can flow. Without such guiding devices, hotspots could result from boiling cooling water in the cavities of the ribs, since the suddenly enlarging cross-section does not ensure adequate replacement of the coolant.
  • the existing guide devices for forced flow a constant flow and thus a constant exchange of the coolant is ensured.
  • the ribs extend at least from a first housing part, which serves as a partition between the channel through which the fluid to be cooled and the channel through which the cooling fluid can flow, into the channel through which the fluid to be cooled and the guide devices are connected to a second housing part arranged, which forms with the first housing part of the flow through the cooling fluid channel.
  • the guide devices are formed by protuberances on the second housing part, which extend into the cavities of the ribs.
  • dead water areas can be reliably prevented in the ribs, in which a uniform flow through the entire cavity is ensured in the ribs.
  • the protuberances extend into the cavities of the ribs such that the cross-section through which the cooling fluid flows in the main flow direction is constant, as a result of which the pressure loss in the coolant channel remains low due to such an embodiment. Furthermore, this in turn prevents dead water areas or turbulences in the region of the ribs due to the uniform flow of the coolant, which in turn increases the rib efficiency.
  • the inner walls of the first and second housing parts which face toward the channel through which the cooling fluid can flow are continuous, so that no cross-sectional jumps occur in the flowed through by the cooling fluid channel, which again reduces the pressure loss and dead water areas are avoided.
  • a heat transfer device improves the cooling efficiency per unit volume due to increased cooling performance of the fins without generating unnecessary pressure losses in the coolant channel. Furthermore, such a heat transfer device without additional manufacturing steps to manufacture, so that no additional costs. With the same desired cooling capacity and the same pump power of the coolant pump can be reduced according to the necessary space. This happens in particular in that the coolant area is now pulled up into the ribs and thus the heat conduction through the cooling rib to the coolant is shortened.
  • FIG. 1 shows a top view of a heat exchanger according to the invention in a sectional view.
  • FIG. 2 shows a top view of an alternative heat exchanger according to the invention in a sectional view.
  • FIG. 3 shows a second alternative embodiment of a heat exchanger according to the invention in a top view and a sectional view.
  • FIG. 4 shows a side view of a detail of a heat transfer device according to the invention in a sectional view.
  • FIG. 5 shows in the same representation one for FIG. 4 alternative embodiment.
  • FIG. 6 shows another one to the FIGS. 4 and 5 Alternative embodiment of a heat transfer device according to the invention in a corresponding representation.
  • FIGS. 1 to 3 show cross sections of three different inventive heat transfer devices, which are composed of several housing parts.
  • the same reference numerals are used in the various figures for the same components.
  • the heat transfer devices consist of a first housing part 1, which is produced for example by die casting and has a partition wall 2, from which ribs 3 extend into a channel 4 through which a fluid to be cooled can flow.
  • This fluid may be, for example, the exhaust gas of an internal combustion engine.
  • a second housing part 5 is placed such that between the first housing part 1 and the second housing part 5 is formed by a flow through a cooling fluid channel 6, so that a heat transfer via the partition wall 2 between the cooling fluid and the fluid to be cooled can take place inside the heat transfer device.
  • the fourth housing part 8 attached to the first housing part 1.
  • the attachment of the housing parts to each other is preferably carried out by friction stir welding.
  • the channels 6 apparently traversed by the cooling fluid, which are formed in cross-section on the opposite sides, are fluidically connected to each other in another plane, so that in the view two channels present after assembly, they form only one channel 6 only needs to be supplied via a coolant inlet 9 with cooling fluid. It should be clear that on the opposite side of the head another nozzle serves as a coolant outlet.
  • the fluid to be cooled preferably flows in and out from the head sides of the heat transfer device. Of course, forms are also conceivable in which the flow-through of the cooling fluid channel 6 completely surrounds the channel 4 through which the fluid to be cooled flows in cross section.
  • cavities 10 are formed in the ribs, which continue in different embodiments in the extension direction of the ribs 3.
  • the cavity 10 extends in an embodiment according to the FIG. 1 from flowing through the cooling fluid channel 6 to shortly before the end of the maximum vertical extent of the rib 3, while in the embodiment according to the FIG. 2 this cavity 10 extends only about halfway up the rib height.
  • an embodiment is selected in which only such a cavity 10 is located in the foot region of the rib 3.
  • a heat transfer device can now be created in different ways. Of course, it is also important to pay attention to the strength of the ribs 3.
  • FIGS. 4 to 6 is each, as in the FIGS. 1 to 3 a first housing part 1 is shown, which has a partition wall 2 and ribs 3, and a second housing part 5, through which the through-flow of the cooling fluid channel 6 is closed.
  • the sections shown here show different embodiments of the formation of the cavities 10 and thus to improve the fin efficiency.
  • the second housing part 5 as a guide device 12 protuberances, which extend from the second housing part 5 in the direction of the respective ribs 3.
  • These protuberances 12 are also in the FIGS. 1 to 3 shown in cross section.
  • each rib 3 a substantially parallelepiped-shaped cavity 10 is created, wherein the cooling fluid is directed through the protuberance 12 into the cavity 10.
  • the inner walls 13 of the two housing parts 1, 5 are formed continuously, so that turbulence of the cooling fluid in the flow-through by cooling fluid channel 6 are largely avoided, which lowers the pressure drop and hotspots in the flow-through by the cooling fluid channel 6, in particular in the region of the cavities 10 of the ribs. 3 prevented.
  • the protuberances 12 so far in the direction of the rib that the flow-through cross-section of the cooling fluid flow-through channel 6 remains substantially constant. This significantly reduces the pressure loss in the radiator and ensures a complete flow. Since at the same time the inner walls 13 of the housing parts 1 and 5 are formed continuously, in comparison to known designs without cavities significantly increased efficiency of the pressure loss is not changed substantially.

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 Semiconductors Or Solid State Devices (AREA)
EP08100462A 2007-02-23 2008-01-15 Dispositif d'échange de chaleur Withdrawn EP1962041A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200710008865 DE102007008865B3 (de) 2007-02-23 2007-02-23 Wärmeübertragungsvorrichtung

Publications (2)

Publication Number Publication Date
EP1962041A2 true EP1962041A2 (fr) 2008-08-27
EP1962041A3 EP1962041A3 (fr) 2011-01-19

Family

ID=39410480

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08100462A Withdrawn EP1962041A3 (fr) 2007-02-23 2008-01-15 Dispositif d'échange de chaleur

Country Status (2)

Country Link
EP (1) EP1962041A3 (fr)
DE (1) DE102007008865B3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012159806A1 (fr) * 2011-05-24 2012-11-29 Pierburg Gmbh Dispositif de transfert de chaleur

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009005879A1 (de) * 2009-01-23 2010-08-05 Semikron Elektronik Gmbh & Co. Kg Kühleinrichtung mit einem Rippenkühlkörper

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8220601U1 (de) 1982-07-19 1987-12-10 Weigelt, Arno-Wolfgang, Ing.(Grad.), 7250 Leonberg Wärmetauscher
DE202006009464U1 (de) 2005-09-23 2006-09-14 Pierburg Gmbh Wärmetauscher

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE438312A (fr) *
JPH0682190A (ja) * 1992-09-01 1994-03-22 Kobe Steel Ltd 強制液冷用アルミニウム冷却板
DE19638794C1 (de) * 1996-09-21 1997-10-30 Mtu Muenchen Gmbh Wärmetauscher

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8220601U1 (de) 1982-07-19 1987-12-10 Weigelt, Arno-Wolfgang, Ing.(Grad.), 7250 Leonberg Wärmetauscher
DE202006009464U1 (de) 2005-09-23 2006-09-14 Pierburg Gmbh Wärmetauscher

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012159806A1 (fr) * 2011-05-24 2012-11-29 Pierburg Gmbh Dispositif de transfert de chaleur
CN103547877A (zh) * 2011-05-24 2014-01-29 皮尔伯格有限责任公司 热交换设备

Also Published As

Publication number Publication date
DE102007008865B3 (de) 2008-08-28
EP1962041A3 (fr) 2011-01-19

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