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WO2007036238A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

Info

Publication number
WO2007036238A1
WO2007036238A1 PCT/EP2005/010303 EP2005010303W WO2007036238A1 WO 2007036238 A1 WO2007036238 A1 WO 2007036238A1 EP 2005010303 W EP2005010303 W EP 2005010303W WO 2007036238 A1 WO2007036238 A1 WO 2007036238A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
ribs
side walls
edge
flow
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.)
Ceased
Application number
PCT/EP2005/010303
Other languages
German (de)
English (en)
Inventor
Oliver Thomer
Dieter Thönnessen
Uwe Rothuysen
Günter Thiel
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
Priority to PCT/EP2005/010303 priority Critical patent/WO2007036238A1/fr
Priority to KR1020060091632A priority patent/KR20070034435A/ko
Priority to JP2006256179A priority patent/JP2007085724A/ja
Priority to US11/534,294 priority patent/US20070068663A1/en
Publication of WO2007036238A1 publication Critical patent/WO2007036238A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F28F1/14—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 and extending longitudinally
    • F28F1/16—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 and extending longitudinally the means being integral with the element, e.g. formed by extrusion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
    • F01N3/04—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust using liquids
    • F01N3/043—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust using liquids without contact between liquid and exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/12—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically the surrounding tube being closed at one end, e.g. return type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • 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
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/02—Streamline-shaped 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
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/14—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes molded
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to a heat exchanger with a coolant-flow channel and a through-flow of a fluid to be cooled channel, which are separated by at least one wall, from which ribs extend in at least one of the two channels.
  • Such heat exchangers are well known and are described in a variety of applications. It. There are both heat exchangers in which the ribs protrude only in the coolant leading channel and heat exchangers whose ribs protrude into the channel through which the fluid to be cooled and heat exchangers with facing ribs in both directions. These ribs significantly improve the heat transfer between the two fluids. In particular, the ribs increase the residence time and the back pressure in the corresponding channel in comparison to designs without ribs. In a heat exchanger which is used as an exhaust gas heat exchanger in internal combustion engines, such ribs can also be used to prevent sooting of the exhaust gas flowed through channel as far as possible.
  • DE 10 2004 045 923 A1 describes heat exchangers whose ribs are shaped differently. They protrude from two inner walls bordering the channel into the channel leading to the fluid to be cooled. All of these ribs have an axisymmetric shape and are employed at least over a portion at an angle to the main flow direction. Both the inflow and the outflow of these ribs is designed with a radius.
  • a disadvantage of such an embodiment is that the production cost is relatively high, since both inner walls must be performed with ribs and secondly There is a high pressure loss through the relatively large existing dust area when the rib flows. The outflow of the ribs presented here is not optimal. Sensitivity to fouling when using the heat exchanger as the exhaust gas heat exchanger remains.
  • the ribs are optimized with respect to the flow, so that the efficiency of the heat exchanger is increased by increasing the heat transfer to the ribs, while the pressure loss in the heat exchanger should remain as low as possible. Furthermore, it is desirable to achieve the lowest possible sooting of the ribs and homogeneity of the fluid to be cooled.
  • each rib has a line-shaped leading edge and at least one line-shaped trailing edge, wherein the leading edge and the at least one trailing edge bound two steadily extending side walls of the rib.
  • This line-shaped leading edge is achieved that is minimized in the flow of the rib, the storage area of the flow in which the speed is reduced to zero, so that a lower pressure loss is achieved.
  • the linear trailing edge in turn has the advantage that an intensive mixing and thus rapid homogenization of the fluid is achieved, which in turn has a temperature exchange and compensation of the entire mass flow result.
  • the continuous side walls cause the formation of a boundary layer, which rests in the region of the rib, so that heat can be exchanged over an extended cooling section. All this increases the efficiency of the heat exchanger.
  • the ribs extend along the main flow direction, thereby minimizing the pressure loss and ensuring that the boundary layer abuts both sides of the rib.
  • a low pressure loss is particularly advantageous when the heat exchanger is used as an exhaust gas heat exchanger in the low pressure region of an internal combustion engine, since in such an application, the existing pressure gradient is very low.
  • adjoining the leading edge and the trailing edge sidewalls of each rib to each other include an angle which is less than or equal to 90 °. This ensures that the pressure loss is sufficiently small and unwanted turbulence and breaks along the cooling section of each rib are avoided.
  • the side walls extending from the leading edge of each rib are arranged substantially wedge-shaped relative to one another in a front region.
  • the angle between tangents on the two side walls in the main flow direction steadily decreases until the side walls in a rear region run parallel to one another. This also leads to an increase in the efficiency, since a separation of the boundary layers over the course of the rib is avoided in this way and a sufficiently long cooling section is available at the rib.
  • the ribs are arranged side by side perpendicular to the main flow direction in rows, wherein the ribs of each row are arranged offset to the next row.
  • the throughflow rate is increased by the small flow cross-sections so that a turbulent flow around the ribs is ensured, whereby a higher wall shear stress and thus a higher heat transfer coefficient ⁇ is achieved, thereby ensuring an increase in the cooling capacity by increasing the heat convection becomes.
  • such a heat exchanger is used as an exhaust gas heat exchanger, the ribs project into the exhaust gas leading channel. This is particularly advantageous since sooting by the resulting flow rates and turbulence is reliably avoided, at the same time a high efficiency and thus a small required size are achieved, which is particularly important in the automotive industry due to the low available space.
  • Figure 1 shows a plan view of a heat exchanger according to the invention in a sectional view.
  • Figure 2 shows a top view of the heat exchanger of Figure 1 in a sectional view.
  • Figure 3 shows a section of the heat exchanger of Figure 1 in an enlarged view.
  • the heat exchanger shown in the drawings which is preferably used as exhaust gas heat exchanger in motor vehicles, consists of an outer housing 1, in which an inner housing 2, which is produced by die-casting, is arranged. Between the inner housing 2 and the outer housing 1, a channel through which the fluid to be cooled flows is formed after assembly. Inside the inner housing 2, a coolant-flow channel 4 is arranged, whose inlet and outlet nozzles are not shown in the drawings and which can be arbitrarily arranged depending on the use. The coolant flowed through channel 4 is limited by walls 5, from which extend ribs 6 in the flowed through by the fluid to be cooled channel 3.
  • the fluid to be cooled through-flow channel 3 is formed such that its inlet 7 is arranged on the same head side as the outlet 8, so that the fluid to be cooled is deflected in a rear region 9 of the heat exchanger by 180 °. Accordingly, the ribs 6 are arranged in this region following the main flow direction.
  • the middle rib 10 extends from the inlet 7 or outlet 8 to a rear region 9, in which the deflection is formed and is designed in its height so that it extends to the outer housing 1, whereby a transverse flow and overflow over a short distance from the inlet 7 to the outlet 8 is prevented.
  • the ribs 6 are seen in the main flow direction, arranged in rows next to each other, with completion of a first row each followed by a second row, the ribs 6 are arranged offset from the ribs 6 of the first row.
  • Such an arrangement of the ribs 6 increases the residence time of the exhaust gas in the heat exchanger and thus its efficiency, since a straight, obstacle-free flow for the fluid to be cooled is no longer possible.
  • FIG. 3 shows a cross-sectional shape of the ribs 6 according to the invention. They have a leading edge 7, which extends from the wall 5 of the inner housing 2 linear to the end of each rib 6 in the channel 3 and can be seen in the figure only as a stagnation point.
  • the adjoining the leading edge 11 side walls 12 of the ribs 6 are designed so that the angle between the two tangents to each side wall 12 of the ribs 6 in a front region 13 steadily decreases until the included angle is 0 ° and thus the both side walls 12 in a rear region 14 parallel to each other.
  • both side walls 12 open onto a respective outflow edge 15, so that a right angle exists between a rear wall 16 of each rib 6 and the side walls 12.
  • the ribs 6 it would be conceivable to allow the ribs 6 to extend in a wedge shape from the leading edge 11 and to allow this wedge shape to subsequently merge continuously into the parallel guidance of the side walls 12.
  • only one trailing edge 15 could be used and thus the ribs 6 are given a kind of hydrofoil shape, wherein in such a shape care should be taken that no stalls would arise in the region of the side walls 12.
  • the length of the ribs 6 is to be designed so that a detachment is avoided. Instead, this is carried out in a defined manner at the outflow edge 15, so that a flow separation in the form of turbulent vortices arises behind the outflow edge 15, which leads to a good homogenization of the exhaust gas in the heat exchanger.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un échangeur de chaleur présentant un canal (4) traversé par un fluide de refroidissement et un canal (3) traversé par un fluide à refroidir, des ailettes (6) faisant saillie au moins dans un des canaux (3, 4). Selon ladite invention, ces ailettes (6) présentent un bord linéaire côté flux entrant (11) et un bord linéaire côté flux sortant (14), les parois latérales (12) entre le bord côté flux entrant (11) et le bord côté flux sortant (14) s'étendant en continu. Ainsi, une couche limite turbulente, qui se forme au niveau des ailettes, se termine en un tourbillon turbulent au niveau du bord côté flux sortant (14), ce qui permet d'augmenter le rendement de l'échangeur de chaleur et d'obtenir une bonne homogénéisation du fluide. Un encrassement également évité de manière fiable.
PCT/EP2005/010303 2005-09-23 2005-09-23 Echangeur de chaleur Ceased WO2007036238A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
PCT/EP2005/010303 WO2007036238A1 (fr) 2005-09-23 2005-09-23 Echangeur de chaleur
KR1020060091632A KR20070034435A (ko) 2005-09-23 2006-09-21 열교환기
JP2006256179A JP2007085724A (ja) 2005-09-23 2006-09-21 熱交換器
US11/534,294 US20070068663A1 (en) 2005-09-23 2006-09-22 Heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2005/010303 WO2007036238A1 (fr) 2005-09-23 2005-09-23 Echangeur de chaleur

Publications (1)

Publication Number Publication Date
WO2007036238A1 true WO2007036238A1 (fr) 2007-04-05

Family

ID=35811513

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/010303 Ceased WO2007036238A1 (fr) 2005-09-23 2005-09-23 Echangeur de chaleur

Country Status (1)

Country Link
WO (1) WO2007036238A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014146158A1 (fr) * 2013-03-19 2014-09-25 Ift Gmbh Dispositif d'échange de chaleur

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2892618A (en) * 1957-04-12 1959-06-30 Ferrotherm Company Heat exchangers and cores and extended surface elements therefor
DE975075C (de) * 1951-07-22 1961-08-03 Gerhard Dipl-Ing Goebel Waermeaustauscher
GB892534A (en) * 1957-10-24 1962-03-28 Richard Kablitz Improvements in and relating to heat exchangers
EP0661414A1 (fr) * 1993-12-28 1995-07-05 Kabushiki Kaisha Toshiba Aube refroidie pour turbine à gaz
DE102004045923A1 (de) * 2003-10-28 2005-05-25 Behr Gmbh & Co. Kg Strömungskanal für einen Wärmeübertrager und Wärmeübertrager mit derartigen Strömungskanälen

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE975075C (de) * 1951-07-22 1961-08-03 Gerhard Dipl-Ing Goebel Waermeaustauscher
US2892618A (en) * 1957-04-12 1959-06-30 Ferrotherm Company Heat exchangers and cores and extended surface elements therefor
GB892534A (en) * 1957-10-24 1962-03-28 Richard Kablitz Improvements in and relating to heat exchangers
EP0661414A1 (fr) * 1993-12-28 1995-07-05 Kabushiki Kaisha Toshiba Aube refroidie pour turbine à gaz
DE102004045923A1 (de) * 2003-10-28 2005-05-25 Behr Gmbh & Co. Kg Strömungskanal für einen Wärmeübertrager und Wärmeübertrager mit derartigen Strömungskanälen

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014146158A1 (fr) * 2013-03-19 2014-09-25 Ift Gmbh Dispositif d'échange de chaleur

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