WO2014198846A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2014198846A1
WO2014198846A1 PCT/EP2014/062275 EP2014062275W WO2014198846A1 WO 2014198846 A1 WO2014198846 A1 WO 2014198846A1 EP 2014062275 W EP2014062275 W EP 2014062275W WO 2014198846 A1 WO2014198846 A1 WO 2014198846A1
Authority
WO
WIPO (PCT)
Prior art keywords
tubes
heat exchanger
fluid
sectional area
tube
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/EP2014/062275
Other languages
German (de)
English (en)
Inventor
Simon HUND
Albrecht Siegel
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
Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Priority to DE112014002833.9T priority Critical patent/DE112014002833A5/de
Publication of WO2014198846A1 publication Critical patent/WO2014198846A1/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
    • 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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/163—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1653—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape
    • F28D7/1661—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 in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing the conduit assemblies having a square or rectangular shape with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • 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
    • 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
    • F28D7/16—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 in parallel spaced relation
    • F28D7/1607—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 in parallel spaced relation with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/08—Assemblies of conduits having different features

Definitions

  • the invention relates to a heat exchanger with a first header, with a second header and with a plurality of tubes, wherein the tubes are respectively received end in one of the collection box and produce a fluid connection between the first header and the second header, wherein a first Number of first tubes is provided, each having a first flow cross-sectional area, and at least a second tube is provided, which has a second flow cross-sectional area.
  • Heat exchangers are used in a variety of ways to transfer wires between two fluids.
  • a first fluid is brought into a heat exchange with a second fluid, whereby the temperature of the one fluid is relatively increased and the temperature of the other fluid is relatively lowered.
  • the fluids used are, for example, air, coolant or a refrigerant.
  • heat exchangers are used in a tube-fin construction. Here a plurality of tubes are spaced from each other between two headers. A medium to be cooled can flow through the pipes, for example, while a medium to be heated flows around the pipes.
  • additional heat transfer elements such as corrugated fins, can be provided between the pipes.
  • a known design provides for a heat exchanger, which is flowed through in a so-called I-flow principle.
  • the fluid flows from a collection box into the pipes and from there into the second collection box.
  • the fluid is introduced from a fluid circuit in the first collection box and discharged from the second collection box.
  • a heat exchanger can be flowed through according to the so-called U-flow principle.
  • a fluid is introduced from a fluid circuit in the first collection box. From there, it flows through a first number of tubes into the second collection box and from there over a second number of tubes back into the first collection box. From there, the fluid is discharged from the first collection box.
  • the first collection box is divided, for example by a partition in two independent areas.
  • the tubes which form the fluid connection from the first collection box into the second collection box usually correspond in size, shape and number to the tubes which form the fluid connection from the second collection box into the first collection box.
  • the U-flowed heat exchanger regularly offers twice the cooling distance compared to a L-flowed heat exchanger, but at the same time it offers only half the flow cross-sectional area. Although this is generally positive for the cooling ⁇ performance of the heat exchanger, but mostly negative for the pressure loss occurring.
  • a disadvantage of the solutions in the prior art is in particular that by using the same pipe dimensions both for the fluid connection from the first to the second collection box and for the fluid connection from the second to the first collection box tubes of the same dimensions and often in the same number are used, which has a negative effect on the resulting pressure loss in the U-flow heat exchanger.
  • An embodiment of the invention relates to a heat exchanger with a first header, with a second header and with a plurality of tubes, wherein the tubes are each end in one of the header boxes and create a fluid connection between the first header and the second header, wherein a first Number of first tubes is provided, each having a first flow cross-sectional area, and at least a second tube is provided, which has a second flow cross-sectional area, wherein the first flow cross-sectional area is substantially smaller than the second flow cross-sectional area.
  • first tubes in each case have a smaller cross section than the cross section of the individual second tube, a plurality of first tubes can be used with the same installation space, in particular in a tube bundle, whereby the resulting Heat exchanger surface increases, which means that a larger cooling line can be generated.
  • the heat exchanger is flowed through by a U-flow principle.
  • Fluid is passed from a collection box over a portion of the pipes in the second collection box before it is returned via the remaining pipes back into the first collection box.
  • This is particularly advantageous if the space specifications allow only such a heat exchanger.
  • the position of the fluid connections to only one collecting box is advantageous.
  • the flow cross-sectional area of the second flow channel is substantially larger than the flow cross-sectional area of the individual first flow channels. As a result, a return flow can be generated with the lowest possible pressure loss.
  • the second flow channel essentially serves to return the fluid to the first collection box.
  • the heat transfer is realized mainly by the first flow channels.
  • the total flow cross-sectional area of the first tubes occupies a proportion of the total cross-sectional area of the heat exchanger which is greater than half, wherein the total cross-sectional area of the heat exchanger is formed by the sum of the flow cross-sectional areas of the first tube and the second tube.
  • the total flow cross-sectional area of the first tubes compared to the total flow cross-sectional area of the heat exchanger is between 50% and 90%, preferably between 60% and 80%, preferably between 70% and 80%.
  • the highest possible proportion of the total flow cross-sectional area of the first flow channels is advantageous in order to be able to realize the largest possible heat transfer.
  • the flow cross-sectional area of the second flow channel must be large enough not to generate too great a pressure loss for the fluid flowing back.
  • the heat exchanger can be flowed through by a first fluid from the first collecting tank through the first pipes to the second collecting tank and from the second collecting tank through the second pipe to the first collecting tank.
  • the heat exchanger can be flowed through by a first fluid from the first collecting tank through the second pipe to the second collecting tank and from the second collecting tank through the first pipes to the first collecting tank.
  • This has the advantage that initially takes place less cooling with a small pressure drop in the second tube and then there is a greater cooling due to the larger heat transfer surface of the many individual first tubes.
  • the heat exchanger can be flowed through by a first fluid, wherein the flow takes place from the first header through the first tubes to the second header and from the second header through the second tube to the first header.
  • the U-flow principle is particularly advantageous when space restrictions provide for the use of a U-flowed Wirmeübertragers.
  • a preferred embodiment is characterized in that the first header has a fluid inlet and a fluid outlet, wherein the first header is divided into a first chamber and a second chamber and the first chamber is in fluid communication with the first tubes and the second chamber is in fluid communication Tube is in fluid communication.
  • a division of the first collecting tank into two chambers is particularly advantageous in order to allow a flow according to the U-flow principle.
  • a fluid-tight separation of the two chambers from each other is particularly advantageous to prevent unwanted leakage currents between the two chambers.
  • first tubes are arranged in a juxtaposition of two mutually adjacent tube rows and the second tube is arranged below or above or laterally of the two tube rows.
  • a housing which receives the first tubes and the second tube, and which is bounded laterally by the two header boxes, wherein the first tubes and the second tube of second fluid within the housing are flowed around while they can be traversed by a first fluid.
  • a fluid such as a coolant
  • the first fluid can be supplied and discharged via a collecting box, wherein a second fluid can be fed into the housing in the region of the first collecting box and can be removed from the housing in the region of the second collecting box.
  • heat transfer elements such as corrugated ribs
  • the heat transfer elements By the heat transfer elements, the heat transfer between the fluid inside the tubes and the fluid flowing around the tubes can be increased. As a result, the cooling capacity of the heat exchanger can be improved overall.
  • the heat exchanger according to the invention is advantageously an exhaust gas cooler in one embodiment.
  • FIG. 1 shows a perspective view of a heat exchanger according to the invention
  • Fig. 2 is a perspective view of a heat exchanger according to the invention, wherein the viewer facing the collection box is not shown, whereby an insight into the flow channels is achieved, and
  • Fig. 3 is a further perspective view of a heat exchanger according to Figure 2 wherein in addition, the housing is not shown, whereby an insight into the heat exchanger is achieved.
  • FIG. 1 shows a perspective view of a heat exchanger 1.
  • the heat exchanger 1 is essentially formed from a housing 2 to which a first collecting box 8 and a second collecting box 9 are connected at the end.
  • the collection box 9 facing away from the viewer has a fluid connection 3 at its upper area.
  • a fluid in the Wirmeübertrager 1 fed or discharged from this.
  • the first collection box 8 is arranged at the end portion of the heat exchanger 1, which faces the viewer.
  • This collecting box 8 has a fluid connection 4, which is in fluid communication with the fluid connection 3 via the housing 2,
  • a fluid can be introduced into the heat exchanger 1 or be discharged from the heat exchanger 1.
  • the collecting box 8 also has a fluid connection 5 and a fluid connection 6 arranged underneath.
  • the fluid connections 5 and 6 are for the Eintial. Discharging a second fluid into the heat exchanger usable.
  • the first fluid is preferably a coolant
  • the second fluid which can be introduced or removed through the fluid ports 5 and 6, is preferably an exhaust gas from an internal combustion engine.
  • the fluid connection 6 has a flange 7, which makes it possible to connect a pipeline, not shown in the figure, to the fluid connection 6.
  • the fluid connection 5 has holding means to which a pipeline can be connected.
  • the fluid which flows into the collecting box 8 via the fluid connection 5 or 6, is distributed within the collecting box to tubes which run inside the housing 2.
  • the exact structure and arrangement of the tubes are shown in the following figures.
  • FIG. 2 shows a perspective view of the heat exchanger 1 according to FIG. 1.
  • the collection box 8 facing the viewer is not shown. This allows a view of the flow channels 11, 12 allows.
  • first flow channels 11 are arranged inside the housing 2 .
  • the first flow channels 11 are arranged in two rows next to each other.
  • a second flow channel 12 is arranged below the two rows of tubes of the first flow channels 11.
  • the second flow channel 12 in this case has a substantially larger flow cross-sectional area than the individual first flow channels 11.
  • the arrangement can also be above or to the side thereof.
  • the sum of the flow cross-sectional areas of the individual first flow channels 11 is greater than the flow cross-sectional area of the second flow channel 12.
  • the sum of the flow cross-sectional areas of the first flow channels 11 has a proportion of more than 50% in the total flow cross-sectional area of the first flow channels 11 and the second flow channel 12 ,
  • the heat exchanger 1 flows through a so-called U-flow principle.
  • the second collection box 9 establishes fluid communication between the uppermost first flow channels 11 and the lower second flow channel 12. Through the second flow channel 12, the fluid finally flows back into the first collection box 8.
  • the first collection box 8 is separated in the interior via a partition in two independent areas.
  • the first upper area stands with the first stream mungskanälen 11 in fluid communication
  • the lower second area is in fluid communication with the lower second flow channel 12.
  • the flow direction through the heat exchanger 1 can also be reversed, so that the second flow channel 12 forms the Hinströmsize between the collecting box 8 and the collecting box 9 and the first flow channels 11, the return flow from the collecting box 9 to the collection box. 8
  • the flow channel 12 has a much lower pressure loss compared to the flow channels 11. This is due to the overall large flow cross-sectional area of the second flow channel 12. The largest part of the cooling of the exhaust gas, which flows through the flow channels 11 and 12, is achieved within the flow channels 11. This is especially re due to the larger wall surface and thus the higher heat transfer area between the exhaust gas and the coolant.
  • the heat exchanger 1 can be influenced by an adaptation of the number of the first flow channels 11 or the size of the second flow channel 12 with regard to the resulting pressure loss and the maximum achievable cooling capacity.
  • FIG. 3 shows a further perspective view of the heat exchanger 1 according to the representation of FIG. 2.
  • the housing 2 is not shown in FIG. It can be seen that the first flow channels 11 are formed by tubes 15 which are arranged in two rows next to one another in a stack arrangement, and the second flow channel 12 is formed by a tube 16.
  • the arrangement of the heat transfer elements is optional.
  • the coolant which can flow into and out of the housing 2 via the fluid connection 3 or 4, can flow around the tubes 15 and 16, respectively. In this way, a maximum possible heat transfer between the exhaust gas in the first and second flow channels 11 and 12 and the cooling medium within the housing 2 is ensured.
  • the number of channels shown and the geometric design of the individual flow channels may differ from the embodiments shown in FIGS. 1 to 3.
  • the embodiment of the heat exchanger shown in FIGS. 1 to 3 is by way of example and should in particular clarify the concept of the invention.
  • Particularly advantageous in the embodiment of the heat exchanger 1 is the recirculation of the exhaust gas through the second flow channel 12, which has a relatively large flow cross-sectional area.
  • the occurring pressure loss for the return flow path can be kept small above this.
  • the heat exchanger 1 shown thus combines the installation space technical advantages of a U-flow heat exchanger 1, which is characterized in particular in that the fluid connections are arranged on only one of the collecting tanks, with the high efficiency of a I - trimströmten heat exchanger.
  • the second flow ungskanai 12 arises for the return flow only a very small pressure loss.
  • the heat exchanger 1 can be built very compact.
  • Figures 1 to 3 are exemplary and are not limiting in nature.

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  • 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 (1) comprenant une première boîte collectrice (8), une deuxième boîte collectrice (9) et une pluralité de tubes (15, 16). Les tubes (15, 16) sont respectivement accueillis par leurs extrémités dans l'une des boîtes collectrices (8, 9) et établissent une liaison fluidique entre la première boîte collectrice (8) et la deuxième boîte collectrice (9). Les tubes d'une première pluralité de premiers tubes (15) possèdent chacun une première section de passage et au moins un deuxième tube (16) possède une deuxième section de passage. La première section de passage est nettement plus petite que la deuxième section de passage.
PCT/EP2014/062275 2013-06-14 2014-06-12 Échangeur de chaleur Ceased WO2014198846A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112014002833.9T DE112014002833A5 (de) 2013-06-14 2014-06-12 Wärmeübertrager

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310211221 DE102013211221A1 (de) 2013-06-14 2013-06-14 Wärmeübertrager
DE102013211221.1 2013-06-14

Publications (1)

Publication Number Publication Date
WO2014198846A1 true WO2014198846A1 (fr) 2014-12-18

Family

ID=50972682

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/062275 Ceased WO2014198846A1 (fr) 2013-06-14 2014-06-12 Échangeur de chaleur

Country Status (2)

Country Link
DE (2) DE102013211221A1 (fr)
WO (1) WO2014198846A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109813164B (zh) * 2017-11-22 2021-09-14 浙江盾安机械有限公司 一种双排折弯换热器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080202739A1 (en) * 2007-02-27 2008-08-28 Barfknecht Robert J 2-Pass heat exchanger including internal bellows assemblies
WO2009044947A1 (fr) * 2007-10-02 2009-04-09 Korens Co., Ltd. Refroidisseur à recirculation de gaz d'échappement
JP2009228930A (ja) * 2008-03-19 2009-10-08 T Rad Co Ltd 熱交換器
EP2194351A1 (fr) * 2008-12-03 2010-06-09 Behr GmbH & Co. KG Refroidisseur de gaz d'échappement avec un filtre intégré pour un moteur à combustion
WO2013080892A1 (fr) * 2011-11-30 2013-06-06 東京ラヂエーター製造株式会社 Ailette interne

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9400687U1 (de) * 1994-01-17 1995-05-18 Thermal-Werke, Wärme-, Kälte-, Klimatechnik GmbH, 68766 Hockenheim Verdampfer für Klimaanlagen in Kraftfahrzeugen mit Mehrkammerflachrohren
DE19515526C1 (de) * 1995-04-27 1996-05-23 Thermal Werke Beteiligungen Gm Flachrohrwärmetauscher mit mindestens zwei Fluten für Kraftfahrzeuge
US7891211B2 (en) * 2005-06-24 2011-02-22 Denso Corporation Cold storage tank unit and refrigeration cycle apparatus using the same
JP2009085569A (ja) * 2007-10-03 2009-04-23 Denso Corp 蒸発器ユニット
JP2009166529A (ja) * 2008-01-11 2009-07-30 Calsonic Kansei Corp 車両用凝縮器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20080202739A1 (en) * 2007-02-27 2008-08-28 Barfknecht Robert J 2-Pass heat exchanger including internal bellows assemblies
WO2009044947A1 (fr) * 2007-10-02 2009-04-09 Korens Co., Ltd. Refroidisseur à recirculation de gaz d'échappement
JP2009228930A (ja) * 2008-03-19 2009-10-08 T Rad Co Ltd 熱交換器
EP2194351A1 (fr) * 2008-12-03 2010-06-09 Behr GmbH & Co. KG Refroidisseur de gaz d'échappement avec un filtre intégré pour un moteur à combustion
WO2013080892A1 (fr) * 2011-11-30 2013-06-06 東京ラヂエーター製造株式会社 Ailette interne

Also Published As

Publication number Publication date
DE102013211221A1 (de) 2014-12-18
DE112014002833A5 (de) 2016-03-10

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