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EP1994349B1 - Unité de transfert thermique - Google Patents

Unité de transfert thermique Download PDF

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Publication number
EP1994349B1
EP1994349B1 EP07712105A EP07712105A EP1994349B1 EP 1994349 B1 EP1994349 B1 EP 1994349B1 EP 07712105 A EP07712105 A EP 07712105A EP 07712105 A EP07712105 A EP 07712105A EP 1994349 B1 EP1994349 B1 EP 1994349B1
Authority
EP
European Patent Office
Prior art keywords
fluid
shut
partial
transmission unit
inlet
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
EP07712105A
Other languages
German (de)
English (en)
Other versions
EP1994349A1 (fr
Inventor
Hans-Ulrich Kühnel
Dieter Jelinek
Peter Heuer
Dieter Thönnessen
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 EP1994349A1 publication Critical patent/EP1994349A1/fr
Application granted granted Critical
Publication of EP1994349B1 publication Critical patent/EP1994349B1/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
    • 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
    • F28D7/106—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 consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28D9/0031—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 paired plates touching each other
    • F28D9/0043—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/0056—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 paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another with U-flow or serpentine-flow inside conduits; with centrally arranged openings on the 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different 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
    • 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
    • F28F2250/06—Derivation channels, e.g. bypass
    • 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

Definitions

  • the invention relates to a heat transfer unit with a channel through which a coolant flows and a channel through which a fluid to be cooled flow, which are separated from one another by a wall, from which ribs extend in at least one of the two channels.
  • Such heat transfer units are used for example for exhaust gas cooling in an exhaust gas recirculation train in an internal combustion engine.
  • the ribs usually protrude into the channel through which the fluid to be cooled flows.
  • the ribs extend from the two opposite sides of the heat transfer unit into the channel, as well as cooling devices in which the ribs only extend from one side into the channel.
  • the ribs may take on different shapes and either extend integrally along the main flow direction or be formed as a single ribs, here both pin and tubular as well as wing-shaped ribs are known.
  • the channel through which the coolant flows can be arranged both within the channel through which the fluid to be cooled and also surround it in cross section.
  • intercoolers serve to reduce the combustion temperatures and thus the resulting nitrogen oxides and exhaust gas cooler for heating the air for faster heating of a passenger compartment or in the exhaust system to reduce the exhaust gas temperature of a gas flowing to a catalyst.
  • exhaust gas recirculation lines are using the exhaust gas cooler the exhaust gas temperatures and thus the combustion temperature in the engine lowered, which in turn pollutant emissions can be reduced.
  • the cooling water of the internal combustion engine serve as a coolant, the cooling water of the internal combustion engine.
  • a heat transfer unit which is arranged in an exhaust gas recirculation system of an internal combustion engine is, for example, from DE 10 2004 019 554 A1 known. This consists of an inner U-shaped flowed through by exhaust gas channel, which is surrounded over the entire cross-section of a coolant flow channel. This is a multi-part die-cast cooler, which has different graduation levels.
  • a charge air cooler is known in which the flow through the radiator can be changed via two flaps. With open flaps, this cooler is flowed through over its entire cross-section in one direction, while with the flaps closed, only the third cross-section is traversed over the third section.
  • the known heat transfer units have only low cooling capacities and cooler efficiencies, in particular at low throughputs and temperature differences. However, especially in the field of exhaust gas recirculation, it may be desirable to further reduce the pollutant emissions to achieve a high cooling capacity at low pressure loss, both at high and at low flow rates.
  • shut-off devices are arranged in the heat transfer unit, wherein when the first fluid part inlet is closed by means of the first shut-off device, the second shut-off device is connected such that the cooling path for the fluid in the heat transfer unit lengthens.
  • the shut-off devices are arranged such that the heat transfer unit is flowed through in part by the second barrier in the opposite direction.
  • the heat transfer unit has two partitions, which cooperate with the shut-off devices in such a way that the entire channel flows through in both switching positions of the shut-off devices, wherein the cooling section extends when the cross-section narrows. It is thus used the entire available cross section of the heat transfer unit in both switching positions of the shut-off, which in turn leads to an increase in efficiency.
  • the cooling section preferably extends substantially to the same extent as the cross section through which it flows decreases. This means that when halving the flow-through cross section, the cooling section is doubled. This can be achieved by using the entire heat transfer unit in both switching positions of the shut-off devices and by multiple deflection.
  • the use of the entire available heat transfer surface in both switching positions of the shut-off to increase the efficiency is achieved in particular by a heat transfer unit, wherein the first partition from the fluid inlet between the first and second fluid part inlet in the main flow direction in the heat transfer unit to the opposite to the fluid inlet End extends and the second partition extends from the fluid outlet between the first and the second Fluidteilauslass in the main flow direction in the heat transfer unit to the fluid outlet opposite end, wherein the first and the second shut-off device are designed as a flap and the flaps at the opposite ends of the heat transfer unit are each arranged between the first and the second partition wall, wherein the flaps are arranged perpendicular to each other in both switching positions.
  • a cooler is formed, in which the flow-through cross-section is halved when the first fluid inlet is closed, at the same time the cooling section is doubled.
  • the first flap is closed, the fluid to be cooled is thus flowed through the narrowed cross section into the heat transfer unit behind the first partition due to the closed position of the second shut-off device deflected by 180 °, behind the central wall in turn deflected by 180 °, which again performed behind the second partition becomes. Only here can the exhaust gas flow out.
  • the first partition wall extends in a U-shape from the fluid inlet between the first and second fluid part inlet in the main flow direction to the second fluid part outlet and the second partition wall extends U-shaped from the fluid outlet between the first and second fluid part outlet in the main flow direction to the first fluid part inlet , wherein the first and the second shut-off device are designed as a flap, wherein the first flap through the first Fluid part inlet is closed and closed by the second flap of the second Fluidteilauslass, the flaps open and close parallel to each other.
  • the flow-through cross-section is divided by three when the first fluid part inlet is closed, and at the same time the cooling section is tripled so that a very good cooling effect is achieved with even lower throughputs or fluid mass flows due to the long existing cooling section and the small cross section.
  • the pressure loss across the cooler can be kept low.
  • a first embodiment of a heat transfer unit 1 which is preferably used as exhaust gas heat exchanger in motor vehicles. It consists of an outer housing 2, in which an inner housing 3, which can be produced, for example, by die-casting, is arranged. Between the inner housing 3 and the outer housing 2, a channel 4 flows through the fluid to be cooled after assembly. In the interior of the inner housing 3, a coolant through-flow channel 5 is arranged, the inlet and outlet nozzles 6, 7 in FIG. 2 are shown and which are arranged in the present embodiment at one to a fluid inlet 8 and a fluid outlet 9 opposite end 10 of the heat transfer unit.
  • the coolant flowed through channel 5 is limited by a circumferential wall 11 in the wall, from which ribs 12 extend in the flowed through by the fluid to be cooled channel 4.
  • the channel 4 through which the fluid to be cooled flows is designed such that its fluid inlet 8 is arranged on the same side of the head as the fluid outlet 9, so that the fluid to be cooled is deflected by 180 ° at the opposite end 10. Accordingly, the ribs 12 are arranged in this region following the main flow direction.
  • the ribs 12 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 12 are arranged offset from the ribs 12 of the first row.
  • Such an arrangement of the ribs 12 increases the residence time of the fluid in the heat transfer unit and thus its efficiency, since a straight, obstacle-free flow is no longer possible for the fluid to be cooled.
  • the heat transfer unit additionally has a first partition wall 14, which extends in a U-shape from the fluid inlet 8 via the end 10 to the fluid outlet 9.
  • This partition wall 14 divides in the present embodiment, the channel 4 in two sub-channels 15 and 16 and thus the fluid inlet 8 and the fluid outlet 9 in two approximately equal fluid part inlets 17, 18 and two fluid part outlets 19, 20.
  • the first fluid part inlet 17 is of a Shut-off device 21 dominated in the form of a flap whose axis of rotation 22 is arranged in the present embodiment in extension to the outer housing 2.
  • both the shut-off device 21 and the partition wall 14 extend over the entire height of the heat transfer unit 1.
  • an exhaust gas recirculation valve is usually formed before the heat transfer unit 1, so that different fluid mass flows or exhaust gas mass flows of the heat transfer unit 1 are supplied. Especially at low exhaust gas mass flows and smaller temperature differences between the exhaust gas and the coolant, the cooling capacity of a heat transfer unit without partition 14 and shut-off device 21 is only very small.
  • the first fluid inlet 17 is closed by the shut-off device 21, so that the entire mass flow flows via the second fluid inlet 18 to the second fluid outlet 20. This is compared to a heat transfer unit 1 without disconnectable channel only half the cross-section available.
  • FIG. 3 A further embodiment of this is in the FIG. 3 shown.
  • two partition walls 23 and 24 are arranged, of which the first partition wall 23 extends from the fluid inlet 8 to the opposite end 10 of the heat transfer unit 1 and the second partition wall 24 extends from the fluid outlet 9 to the opposite end 10 of the heat transfer unit 1 extends.
  • Both partitions 23, 24 terminate at a sufficient distance from the end 10, so that when closing one of the fluid part inlets 17, 18 a sufficient cross-section for the flow of fluid behind the ends of the partition walls 23 and 24 and the outer housing 2 is available.
  • a shut-off device in the form of a flap 27, 28 is mounted between the respective ends of the two partitions 23, 24 in extension to the wall 13 .
  • the width of the flaps 27, 28 corresponds to the distance between the two partitions 23, 24.
  • the width of the end of the wall 13 of the axes of rotation 25, 26 each half the width of such a flap 27, 28, so that the first flap 27 in its first position, the first fluid part inlet 17 and the first Fluidteilauslass 19 shuts off, while the second flap 28 is disposed in its first end position offset by 90 ° to the first flap 27 and thus rests in its width with one end against the wall 13 and abuts against the outer housing 2 with its other end. In its second position, the first flap 27 abuts with its two ends against the partitions 23 and 24.
  • the first shut-off device 27 in a position in which it rests against the two partitions 23, 24, the first fluid part inlet 17 is closed.
  • the fluid mass flow thus enters via the second fluid part inlet 18 in the sub-channel 16 and from here to the opposite end 10 of the heat transfer unit 1.
  • the second shut-off device 28 prevents now by their above-mentioned first position a fluid mass flow over the extension of the wall 13 addition. Consequently, the fluid mass flow undergoes a 180 ° turn and passes behind the dividing wall 23 into the partial passage 15, but flows through it in the opposite direction, ie in the direction of the first fluid inlet inlet 10.
  • FIG. 4 shows a further alternative heat transfer unit 1 in which again two partitions 29, 30 and two shut-off devices 31, 32 are used.
  • first partition wall 29 runs the first partition wall 29 from the fluid inlet 8 U-shaped to the fluid outlet 9 and ends at a distance in front of the fluid outlet 9, which corresponds to half the width of the shut-32.
  • parallel to the U-shaped second partition wall 30 extends from the fluid outlet 9 in the direction of the fluid inlet 8 where it in turn ends at a distance from the fluid inlet 8, which corresponds to half the width of the shut-off device 31.
  • These two partitions 29, 30 are arranged so that the fluid inlet 8 and the fluid outlet 9 are approximately divided in their cross-section and in their width.
  • shut-off devices 31, 32 are arranged on axes of rotation 33, 34, which are arranged in extension to the ends of the partitions 29, 30 in the region of the fluid part inlets 17, 18 or fluid part outlets 19, 20.
  • shut-off devices 31, 32 open, that is to say when the flap extension extends in the direction of the dividing walls 29, 30, the usual fluid mass flow is U-shaped through the entire cross section from the fluid inlet 8 to the fluid outlet 9, reliably avoiding excessive pressure losses at high throughputs.
  • the illustrated embodiments of the heat transfer unit allow use with very good cooling performance and cooler efficiencies over a wide range of throughput and temperature. At the same time, the pressure loss across the cooler is kept as small as possible.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • General Details Of Gearings (AREA)
  • Exhaust-Gas Circulating Devices (AREA)

Claims (6)

  1. Unité de transfert thermique comprenant un canal (5) traversé par un produit de refroidissement et un canal (4) traversé par un fluide à refroidir, qui sont séparés par une première paroi (11) d'où s'étendent des nervures (12) dans au moins un des deux canaux (4, 5), ledit canal (4) traversé par ledit fluide à refroidir comprenant une entrée de fluide (8) et une sortie de fluide (9), et ladite unité de transfert thermique (1) comprenant une deuxième paroi (13) qui sépare ladite entrée de fluide (8) de ladite sortie de fluide (9) et s'étend jusqu'à avant une extrémité (10) de ladite unité de transfert thermique (1) opposée à ladite entrée de fluide (8) ou ladite sortie de fluide (9), respectivement, caractérisée en ce qu'une paroi de séparation (14; 23, 24; 29, 30) s'étendant dans la direction d'écoulement divise ledit canal (4) en un premier et un deuxième canal partiel (15, 16) avec une première entrée de fluide partielle (17) et une deuxième entrée de fluide partielle (18) et une première sortie de fluide partielle (19) et une deuxième sortie de fluide partielle (20), au moins ladite première entrée de fluide partielle (17) étant obturable à l'aide d'un moyen d'obturation (21; 27; 31) de sorte que ladite unité de transfert thermique (1) est traversée en forme de U si le premier moyen d'obturation (21; 27; 31) est ouvert, et qu'elle est traversée au moins partiellement en forme de U si ledit premier moyen d'obturation (21; 27; 31) est fermé.
  2. Unité de transfert thermique selon la revendication 1, caractérisée en ce que deux moyens d'obturation (27, 28; 31, 32) sont disposés dans ladite unité de transfert thermique (1), où, lors de l'obturation du ladite première entrée de fluide (17) par ledit premier moyen d'obturation (27; 31), ledit deuxième moyen d'obturation (28; 32) est commuté de sorte que le trajet de refroidissement du fluide dans ladite unité de transfert thermique(1) est rallongé.
  3. Unité de transfert thermique selon la revendication 2, caractérisée en ce que ladite unité de transfert thermique (1) comprend deux parois de séparation (23, 23; 29, 30), qui coopèrent avec les moyen d'obturation (27, 28; 31, 32) de sorte que tout le canal (4) est traversé dans les deux positions de commutation desdits moyens d'obturation (27, 28; 31, 32), ledit trajet de refroidissement étant rallongé si la section transversale est rétrécie.
  4. Unité de transfert thermique selon la revendication 3, caractérisée en ce que le trajet de refroidissement est rallongé sensiblement d'autant que la section transversale traversée est réduite.
  5. Unité de transfert thermique selon les revendications 3 ou 4, caractérisée en ce que la première paroi de séparation (23) s'étend, à partir de l'entrée de fluide (8), entre ladite première et ladite deuxième entrée de fluide partielle (17, 18) selon la direction d'écoulement principale dans ladite unité de transfert thermique (1) jusqu'à avant l'extrémité (10) opposée à l'entrée de fluide (8), et la deuxième paroi de séparation (24) s'étend, à partir de la sortie de fluide (9), entre ladite première et ladite deuxième sortie de fluide partielle (19, 20) selon la direction d'écoulement principale dans ladite unité de transfert thermique (1) jusqu'à avant l'extrémité (10) opposée à la sortie de fluide (9), ledit premier et ledit deuxième moyen d'obturation (27, 28) étant configurés comme clapets, et les clapets (27, 28) sont disposés aux extrémités opposées de ladite unité de transfert thermique (1), respectivement entre la première et la deuxième paroi de séparation (23, 24), lesdits clapets (27, 28) étant disposés perpendiculairement l'un par rapport à l'autre dans les deux positions de commutation.
  6. Unité de transfert thermique selon les revendications 3 ou 4, caractérisée en ce que la première paroi de séparation (29) s'étend en forme de U à partir de ladite entrée de fluide (8) entre ladite première et ladite deuxième entrée de fluide partielle (17, 18) selon la direction d'écoulement principale jusqu'à avant ladite deuxième sortie de fluide partielle (20), et la deuxième paroi de séparation (30) s'étend en forme de U à partir de ladite sortie de fluide (9) entre ladite première et ladite deuxième sortie de fluide partielle (19, 20) selon la direction d'écoulement principale jusqu'à avant ladite première entrée de fluide partielle (17), ledit premier et ledit deuxième moyen d'obturation (31, 32) étant configurés comme clapets, ladite première entrée de fluide partielle (17) étant obturable par ledit premier clapet (31) et ladite deuxième sortie de fluide partielle (20) étant obturable par ledit deuxième clapet (32), lesdits clapets (31, 32) ouvrant et fermant en parallèle.
EP07712105A 2006-03-16 2007-01-25 Unité de transfert thermique Not-in-force EP1994349B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006012219.4A DE102006012219B4 (de) 2006-03-16 2006-03-16 Wärmeübertragungseinheit mit einem verschließbaren Fluidteileinlass
PCT/EP2007/050720 WO2007104595A1 (fr) 2006-03-16 2007-01-25 Unite de transfert thermique

Publications (2)

Publication Number Publication Date
EP1994349A1 EP1994349A1 (fr) 2008-11-26
EP1994349B1 true EP1994349B1 (fr) 2011-10-26

Family

ID=37944189

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07712105A Not-in-force EP1994349B1 (fr) 2006-03-16 2007-01-25 Unité de transfert thermique

Country Status (7)

Country Link
US (1) US8403031B2 (fr)
EP (1) EP1994349B1 (fr)
JP (1) JP5039065B2 (fr)
AT (1) ATE530868T1 (fr)
DE (1) DE102006012219B4 (fr)
ES (1) ES2373064T3 (fr)
WO (1) WO2007104595A1 (fr)

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Also Published As

Publication number Publication date
WO2007104595A1 (fr) 2007-09-20
DE102006012219A1 (de) 2007-09-27
ES2373064T3 (es) 2012-01-31
JP5039065B2 (ja) 2012-10-03
JP2009529650A (ja) 2009-08-20
US20090183861A1 (en) 2009-07-23
US8403031B2 (en) 2013-03-26
EP1994349A1 (fr) 2008-11-26
ATE530868T1 (de) 2011-11-15
DE102006012219B4 (de) 2018-04-05

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