EP0633444A2 - Echangeur de chaleur avec plusieurs tubes d'échange en parallèle - Google Patents

Echangeur de chaleur avec plusieurs tubes d'échange en parallèle Download PDF

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Publication number
EP0633444A2
EP0633444A2 EP94110457A EP94110457A EP0633444A2 EP 0633444 A2 EP0633444 A2 EP 0633444A2 EP 94110457 A EP94110457 A EP 94110457A EP 94110457 A EP94110457 A EP 94110457A EP 0633444 A2 EP0633444 A2 EP 0633444A2
Authority
EP
European Patent Office
Prior art keywords
ribs
heat exchanger
openings
cross
exchanger 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.)
Granted
Application number
EP94110457A
Other languages
German (de)
English (en)
Other versions
EP0633444A3 (fr
EP0633444B1 (fr
Inventor
Burkhard Trage
Harald Sassmann
Wolfgang Holten
Miroslav Podhorsky
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.)
Balcke Duerr GmbH
Babcock Borsig AG
Original Assignee
Balcke Duerr AG
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
Priority claimed from DE4322405A external-priority patent/DE4322405C2/de
Application filed by Balcke Duerr AG filed Critical Balcke Duerr AG
Publication of EP0633444A2 publication Critical patent/EP0633444A2/fr
Publication of EP0633444A3 publication Critical patent/EP0633444A3/fr
Application granted granted Critical
Publication of EP0633444B1 publication Critical patent/EP0633444B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • 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
    • F28F2215/08—Fins with openings, e.g. louvers

Definitions

  • the invention relates to a heat exchanger comprising a plurality of exchanger tubes arranged parallel to one another, the cross section of which has a large width in relation to the height for the passage of one of the media involved in the heat exchange, fins being fastened to each of the two flat sides of the exchanger tubes, which ribs are deflected from a multiple meandering shape Rib band are formed.
  • a heat exchanger of this type is known from DE 40 39 293 A1.
  • the exchanger tubes used here each consist of two half-shells, which are provided with the fins in a suitable device. Then two half-shells are connected to each other, so that exchanger tubes with the cross-sectional area of an elongated oval are formed.
  • the ribs in the known heat exchanger are formed from a ribbed belt which, before being fastened to the flat sides of the respective exchanger tube, is given the required rib shape by multiple, meandering deflections. The ribbed belt thus formed is then attached to the respective flat side of the exchanger tube.
  • the ribs which are produced from an endless ribbed belt and each form a channel that is continuously formed over the length of the flat sides, are provided with features in the form of lateral offsets. In this way an increased degree of turbulence is to be generated in the medium flowing through the channels, which is suitable for increasing the heat transfer.
  • a disadvantage of heat exchangers of this type is the relatively high tendency towards contamination in the channels formed by the ribs. Due to the formations in the form of individual lateral offsets, this tendency to become contaminated is increased even further, since dirt particles can attach themselves particularly easily to these locations, which can result in the progressive operation of the heat exchanger until the relevant channel is completely closed. This causes an undesirable local deterioration in the heat transfer behavior of the heat exchanger.
  • the invention is therefore based on the object of further developing the known heat exchanger in such a way that the influence of any contamination on the heat transfer performance of the heat exchanger is reduced.
  • the ribs are provided with a plurality of openings, the opening cross-sections of which each have at least the size of the cross-section through which flow passes between two adjacent ribs.
  • the openings are arranged in the region of the deflections of the ribs facing away from the flat side of the exchange tube, so that a material exchange with the medium flowing through the ribs of the respectively adjacent exchanger tube is possible. This also ensures that the losses caused by contamination are distributed more evenly over the individual exchanger tubes of the heat exchanger. This also contributes if the openings overlap with the openings of the ribs of the adjacent exchanger tube.
  • the flow exchange between the cross sections subdivided by the ribs is further improved in that the side faces of the ribs in the region of the rib base are provided with additional openings, the opening cross sections of which are each smaller than the size of the cross section through which flow passes between two adjacent ribs.
  • the additional openings are preferably located halfway between two successive openings.
  • a particularly good connection between the ribbed belt and the respective exchanger tube is achieved if, according to a preferred embodiment, the meandering of the ribbed belt is rectangular, so that the deflections are flat surfaces for abutment on the flat sides of the exchanger tube or on the correspondingly designed surfaces of the ribbed belt of the adjacent one Form the exchanger tube. This can also improve the mutual support between adjacent exchanger tubes.
  • Another embodiment of the heat exchanger is characterized by partly lowered, partly raised shaped features in the side surfaces of the Ribs. These characteristics generate or intensify turbulence of the medium flowing through, as a result of which the heat transfer capacity can be increased further.
  • the deflections are fastened to the flat sides of the exchanger tube via a linear, continuous weld. In this way, there is a particularly good metallic connection between the parts, and thus a high heat transfer between the exchanger tube and the fins.
  • the deflections are preferably welded to the respective flat side by means of a capacitor discharge welding process.
  • This welding process enables the broad sides of the base body to adapt to the contour of the respective fin base without a gap when the fin plate and the exchanger tube are brought together.
  • the pressure required for this is generated by two electrodes, which are part of the capacitor discharge welding machine. While one electrode moves into the fin base area between two adjacent ribs, the other electrode rests on the inside of the base body and forms an abutment. In this way, a gapless contact of the parts to be connected is ensured, so that after the capacitors of the capacitor discharge welding device have been discharged, a linear fastening of the ribs on the base body and thus very good heat transfer between these parts is achieved.
  • the heat exchanger shown in Fig. 1 consists of exchanger tubes 1, which are arranged parallel to each other in the manner of a package. For reasons of clarity, only two such exchanger tubes 1 are shown in FIG. 1.
  • Fig. 1 shows that the cross section of the exchanger tubes 1 for the passage of one of the media involved in the heat exchange has a large width B in relation to the height H.
  • the longitudinal edges of the exchanger tube 1 thus formed are rounded, so that the cross section of an elongated oval is obtained overall.
  • the respective other medium is guided in cross flow over the outer flat sides 2 of the exchanger tubes 1.
  • 1 ribs 3 are arranged on the respective flat sides 2 of the exchanger tubes involved in order to enlarge the effective heat exchange surfaces.
  • the ribs 3 are produced from an endless sheet by repeated bending, so that, viewed in the longitudinal direction of the exchanger tube 1, the ribs 3 line up in a meandering manner. This can be seen particularly well in FIG. 2.
  • the meandering of the ribbed belt 4 thus formed has a rectangular shape, so that the deflections 5 facing the exchanger tube 1 and those facing away from the exchanger tube 1 each form flat surfaces 6.
  • the surfaces 6 serve for a particularly good connection of the fin base area to the flat side 2 of the exchanger tube 1.
  • the material for the fin band 4 is, for example, sheet steel with a thickness of 0.1 to 0.4 mm, which is coated on both sides with a thin aluminum layer .
  • the ribs 3 consisting of the meandering deflected ribbed belt 4 are located on both sides of the exchanger tubes 1.
  • the exchanger tubes 1 designed in this way can then be put together to form any packages, with the fastening and spacing of the individual exchanger tubes 1 from one another at their ends.
  • the deflections 5 at the end of the rib 3 should have the smallest possible distance from the opposite deflections 5 of the adjacent exchanger tube 1. However, the distance must not be so small that there is a risk of contact between the ribs 3 of the adjacent exchanger tubes 1.
  • a capacitor discharge welding process is used to connect the fin base area to the flat side 2 of the exchanger tube, which is explained below with reference to FIGS. 3, 4 and 5.
  • Capacitor discharge welding is a special type of resistance welding in which the energy required during welding is not drawn directly from the mains via a transformer, but from a capacitor battery that is charged as energy storage outside of the welding time.
  • the advantage of capacitor discharge welding is the suitability to use different materials, e.g. Steel / aluminum. This method can also be used to weld surface-treated materials, e.g. galvanized or aluminized sheets without damaging the surface.
  • the capacitor discharge welding process uses two mutually independent electrodes 7, 8.
  • the upper electrode 7 is provided five times and consists of disk-shaped individual electrodes made of a suitable electrode material, e.g. CuCrZr.
  • the lower electrode 8 is designed as a plate which extends over the entire width of the exchanger tube 1 and in this case has exactly its inner profile. In this way, the lower electrode 8 also serves to guide the base body of the exchanger tube 1 during the welding process. In particular, however, the lower electrode 8 forms an abutment for the pressing forces generated by the upper electrodes 7. For this purpose, the lower electrode 8 is supported in a suitable manner with the interposition of insulation on the welding device used.
  • the alignment of the upper electrodes 7 is such that, with their narrow end faces, they can move exactly between two adjacent ribs 3 until they come into contact with the rib foot region arranged in between on the inside of the surface 6.
  • Spring elements 7a cause a defined pressing force which is absorbed by the lower electrode 8 serving as an abutment.
  • the capacitors of the welding device are discharged, as a result of which a high level of energy flows briefly from the upper electrodes 7 to the lower electrode 8. Due to the concentration of the welding energy on the welding zone and the very short welding time of 1 to 10 milliseconds, there is no significant heating of the components.
  • the finished heat exchanger parts come out of the machine practically cold after welding, therefore they retain their shape and show no tendency to warp or change shape.
  • FIGS. 4 and 5 show exchanger tube 1 and fins 3 immediately before they are joined, the surfaces that come into contact with one another being provided with a surface structure designed in the pattern repeat.
  • the outer flat side 2 of the exchanger tube 1 is provided with a fine, uniform corrugation 8 with groove depths of approximately 0.1 to 0.3 mm.
  • the ribbed belt 4 is shown as a continuous, meandering folded sheet without further structures.
  • the ribs do not form channels which are closed over their entire length, but rather are provided with openings 9 at regular intervals, as is shown by the exact representations in FIGS. 1, 2, 4 and 5.
  • These openings 9 are arranged in the region of the deflections 5 facing away from the flat side 2 of the exchanger tube 1, i.e. in the area of the end of the ribs. Via these openings 9, a material exchange can take place with the medium flowing through the ribs 3 of the respectively adjacent exchanger tube 1.
  • the mode of operation is explained below with reference to FIG. 1:
  • the flow arrows A illustrate the flow entry into the area of the ribs.
  • contamination S in one of the cross sections. Since it is not possible for the flow to pass in this area, the flow through this cross section would be completely prevented in a heat exchanger of the known type.
  • the openings 9 provided according to the invention, however, the flow can take the path of a deflection U go. In this case, the flow passes through the opening 9 arranged in front of the obstacle into that cross section which is formed by the ribs 3 of the respectively adjacent exchanger tube 1. A corresponding increase in flow velocity then takes place here. After bypassing the obstacle, part of the flow can then flow back into the original cross section via the subsequent opening 9, so that the flow ultimately leaves the heat exchanger evenly.
  • each of the openings 9 has at least the size of the cross section Q through which flow takes place between two adjacent ribs 3.
  • the individual ribs 3 are provided with additional geometric structures which serve to mix the medium flowing through or flowing past or to generate turbulence.
  • features 10 in the form of lateral bulges are provided in the side surfaces of the ribs 3, which extend alternately to one side and to the other side of the respective rib 3. These characteristics 10 bring about a considerable increase in turbulence of the medium flowing past.
  • additional openings 11 are also provided. These are located in the side surfaces of the ribs 3 in the area of the base of the rib. Their opening cross-section is significantly smaller than the opening cross-section of the openings 9, in particular smaller than the size of the cross-section Q through which flow passes between two adjacent ribs 3.
  • FIG. 1 shows that the additional openings 11 are each halfway between two successive openings 9.

Landscapes

  • 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)
  • Separation By Low-Temperature Treatments (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Power Steering Mechanism (AREA)
EP94110457A 1993-07-06 1994-07-05 Echangeur de chaleur avec plusieurs tubes d'échange en parallèle Expired - Lifetime EP0633444B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4322405 1993-07-06
DE4322405A DE4322405C2 (de) 1993-07-06 1993-07-06 Verfahren zur Herstellung von Wärmetauscherelementen
DE9310827U 1993-07-20
DE9310827U DE9310827U1 (de) 1993-07-06 1993-07-20 Waermetauscher aus mehreren parallel zueinander angeordneten austauscherrohren

Publications (3)

Publication Number Publication Date
EP0633444A2 true EP0633444A2 (fr) 1995-01-11
EP0633444A3 EP0633444A3 (fr) 1995-04-26
EP0633444B1 EP0633444B1 (fr) 1998-05-20

Family

ID=25927414

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94110457A Expired - Lifetime EP0633444B1 (fr) 1993-07-06 1994-07-05 Echangeur de chaleur avec plusieurs tubes d'échange en parallèle

Country Status (14)

Country Link
US (1) US5429185A (fr)
EP (1) EP0633444B1 (fr)
JP (1) JPH07151481A (fr)
KR (1) KR950003781A (fr)
CN (1) CN1102475A (fr)
AT (1) ATE166450T1 (fr)
AU (1) AU6601494A (fr)
BR (1) BR9402643A (fr)
CA (1) CA2127413A1 (fr)
DE (2) DE9310827U1 (fr)
IL (1) IL110148A (fr)
IN (1) IN190153B (fr)
RU (1) RU2085822C1 (fr)
TW (1) TW247345B (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19813989A1 (de) * 1998-03-28 1999-09-30 Behr Gmbh & Co Wärmetauscher
WO2014206455A1 (fr) * 2013-06-26 2014-12-31 L&P Swiss Holding Ag Lombostat et son procédé de production

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6174454B1 (en) 1999-01-29 2001-01-16 National Science Council Slurry formulation for selective CMP of organic spin-on-glass insulating layer with low dielectric constant
GB2354817A (en) * 1999-09-29 2001-04-04 Ford Motor Co Fin construction
FR2824895B1 (fr) * 2001-05-18 2005-12-16 Air Liquide Ailette ondulee a persiennes pour echangeur de chaleur a plaques, et echangeur a plaques muni de telles ailettes
DE10328748B4 (de) * 2003-06-25 2017-12-14 Mahle International Gmbh Wärmeübertrager, insbesondere Ladeluftkühler für Nutzfahrzeuge
US20070012430A1 (en) * 2005-07-18 2007-01-18 Duke Brian E Heat exchangers with corrugated heat exchange elements of improved strength
DE102009032166B3 (de) * 2009-07-08 2010-09-30 Handtmann Systemtechnik Gmbh & Co. Kg Verfahren zum Verbinden von Wärmetauscherkomponenten durch Schweißen und Löten
JP2012007778A (ja) * 2010-06-23 2012-01-12 Komatsu Ltd 熱交換器
CN105484853B (zh) * 2014-09-17 2018-07-06 泰安鼎鑫冷却器有限公司 一种双波内翅片结构中冷器
KR20160071617A (ko) 2014-12-12 2016-06-22 정주옥 커버링용 스핀들 장치
KR101910229B1 (ko) 2015-06-08 2018-10-19 정주옥 스핀들 장치용 커버체
WO2020149155A1 (fr) * 2019-01-15 2020-07-23 株式会社ティラド Échangeur de chaleur du type à ailettes ondulées
JP2022070491A (ja) * 2020-10-27 2022-05-13 有限会社和氣製作所 熱交換器
CN113280544A (zh) * 2021-05-14 2021-08-20 章世燕 食用冰发生器

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Publication number Priority date Publication date Assignee Title
GB745936A (en) * 1953-01-28 1956-03-07 William Helmore Improvements in or relating to corrugated sheet material
GB1254372A (en) * 1969-03-04 1971-11-24 Rootes Motors Ltd Improvements in or relating to methods of making heat exchangers
US4256177A (en) * 1978-11-09 1981-03-17 Modine Manufacturing Company Heat exchanger
AT380104B (de) * 1982-10-15 1986-04-10 Stelrad Radiatoren & Kessel Plattenradiator
JPS63318487A (ja) * 1987-06-22 1988-12-27 Matsushita Refrig Co フィン付熱交換器
NL8900293A (nl) * 1989-02-07 1990-09-03 Lummus Heat Transfer Systems B Warmtewisselingsbuis en warmtewisselaar.
EP0546334A1 (fr) * 1991-12-11 1993-06-16 BDAG Balcke-Dürr Aktiengesellschaft Procédé et dispositif pour fabriquer des élément, échangeurs de chaleur, et élément d'un échangeur de chaleur

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BE542365A (fr) * 1900-01-01
DE4957C (de) * G. HEMPE, Maschinentechniker, in Buckau bei Magdeburg, Wilhelmstrafse 14 Wassermesser
AT79663B (de) * 1916-03-18 1919-12-29 Johann Schandl Lamellenkühler für Verbrennungskraftmaschinen.
US2035665A (en) * 1932-04-11 1936-03-31 Oscar C Palmer Radiator construction
DE2352950A1 (de) * 1973-10-23 1975-04-30 Volkswagenwerk Ag Fluessigkeitsdurchstroemter leichtmetall-waermetauscher
DE2813747A1 (de) * 1978-03-30 1979-10-04 Thermal Waerme Kaelte Klima Waermetauscherlamelle und anwendungen derselben
DE3315314C2 (de) * 1983-04-27 1986-11-20 Schäfer Werke GmbH, 5908 Neunkirchen Schweißmaschine zur Durchführung des Kondensatorentladungsschweißens
DE3620345A1 (de) * 1986-06-18 1987-12-23 Weinsberg Karosseriewerke Waermetauscherelement
DE4039293C3 (de) * 1990-12-08 1995-03-23 Gea Luftkuehler Happel Gmbh Wärmeaustauscher
DE4042195A1 (de) * 1990-12-29 1992-07-02 Bosch Gmbh Robert Waermeuebertrage und verfahren zur herstellung einer lamelle fuer einen waermeuebertrager
DE4219619C1 (de) * 1992-06-16 1994-01-27 Fraunhofer Ges Forschung Verfahren und Vorrichtung zum Fügen einer kontinuierlich geförderten stromleitenden Materialbahn

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB745936A (en) * 1953-01-28 1956-03-07 William Helmore Improvements in or relating to corrugated sheet material
GB1254372A (en) * 1969-03-04 1971-11-24 Rootes Motors Ltd Improvements in or relating to methods of making heat exchangers
US4256177A (en) * 1978-11-09 1981-03-17 Modine Manufacturing Company Heat exchanger
AT380104B (de) * 1982-10-15 1986-04-10 Stelrad Radiatoren & Kessel Plattenradiator
JPS63318487A (ja) * 1987-06-22 1988-12-27 Matsushita Refrig Co フィン付熱交換器
NL8900293A (nl) * 1989-02-07 1990-09-03 Lummus Heat Transfer Systems B Warmtewisselingsbuis en warmtewisselaar.
EP0546334A1 (fr) * 1991-12-11 1993-06-16 BDAG Balcke-Dürr Aktiengesellschaft Procédé et dispositif pour fabriquer des élément, échangeurs de chaleur, et élément d'un échangeur de chaleur

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 13, no. 161 (M-815) 18. April 1989 & JP-A-63 318 487 (MATSUSHITA REFRIGERATION CO.) 27. Dezember 1988 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19813989A1 (de) * 1998-03-28 1999-09-30 Behr Gmbh & Co Wärmetauscher
WO2014206455A1 (fr) * 2013-06-26 2014-12-31 L&P Swiss Holding Ag Lombostat et son procédé de production

Also Published As

Publication number Publication date
JPH07151481A (ja) 1995-06-16
RU94023243A (ru) 1996-05-10
TW247345B (fr) 1995-05-11
DE9310827U1 (de) 1993-09-23
IL110148A0 (en) 1994-10-07
AU6601494A (en) 1995-01-19
DE59405984D1 (de) 1998-06-25
RU2085822C1 (ru) 1997-07-27
CA2127413A1 (fr) 1995-01-07
IL110148A (en) 1997-06-10
EP0633444A3 (fr) 1995-04-26
KR950003781A (ko) 1995-02-17
US5429185A (en) 1995-07-04
BR9402643A (pt) 1995-04-04
EP0633444B1 (fr) 1998-05-20
CN1102475A (zh) 1995-05-10
IN190153B (fr) 2003-06-21
ATE166450T1 (de) 1998-06-15

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