EP1646836A1 - Rohrbündelwärmetauscher - Google Patents
RohrbündelwärmetauscherInfo
- Publication number
- EP1646836A1 EP1646836A1 EP04738868A EP04738868A EP1646836A1 EP 1646836 A1 EP1646836 A1 EP 1646836A1 EP 04738868 A EP04738868 A EP 04738868A EP 04738868 A EP04738868 A EP 04738868A EP 1646836 A1 EP1646836 A1 EP 1646836A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- channel
- tubes
- heat exchanger
- rings
- tube bundle
- 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
Links
- 238000010438 heat treatment Methods 0.000 claims abstract description 29
- 239000002826 coolant Substances 0.000 claims abstract description 24
- 239000007789 gas Substances 0.000 description 33
- 230000005284 excitation Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- OKKJLVBELUTLKV-UHFFFAOYSA-N Methanol Chemical compound OC OKKJLVBELUTLKV-UHFFFAOYSA-N 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- PEDCQBHIVMGVHV-UHFFFAOYSA-N Glycerine Chemical compound OCC(O)CO PEDCQBHIVMGVHV-UHFFFAOYSA-N 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- 235000012093 Myrtus ugni Nutrition 0.000 description 1
- 244000061461 Tema Species 0.000 description 1
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 239000003245 coal Substances 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000002309 gasification Methods 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
-
- 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
-
- 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
- F28D7/06—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 having a single U-bend
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/007—Auxiliary supports for elements
- F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
- F28F9/0131—Auxiliary supports for elements for tubes or tube-assemblies formed by plates
Definitions
- the invention relates to a tube bundle heat exchanger with at least one channel carrying a heating or cooling medium, in particular a heating gas channel, the tubes of the tube bundles running essentially axially parallel to the longitudinal axis of the channel through the channel and the heating or cooling medium through on the respective jacket walls of the channel, alternately arranged and fastened rings and disks, viewed in the axial direction of the channel, are guided in zigzag fashion through the channel, which has an essentially annular cross section.
- a heating or cooling medium in particular a heating gas channel
- tube bundle heat exchangers are required, which are flowed with different gaseous and / or liquid media on the tube and shell side (channel side).
- baffles rings and washers
- baffles are installed at certain intervals, with the help of which baffles directed between the tube bundle tubes or heating surface tubes are used between the baffle plates Flow of the heating or cooling medium is generated.
- This flow component can act on the heating surface tubes with pulsating forces, so that they are excited to vibrate and in the worst case are mechanically stressed by constant vibration, especially in the resonance area of the tubes.
- the natural frequency of the pipes is mainly determined by the pipe diameter, the wall thickness of the pipes and the distance between the support points (pipe plates, baffle plates that support a pipe).
- the excitation frequency of the medium depends on the cross component of the speed of the medium and the pipe pitch.
- a match of the natural frequency of the pipes with the excitation vibration frequency leads to a vibration resonance with uncontrolled large vibration amplitudes and consequently to a high mechanical load on the pipes and the risk of cracks or other mechanical damage.
- the danger of a resonance vibration is generally excluded with the help of a vibration analysis, which is to be carried out, for example, according to the TEMA standard (Tubular Exchanger Manufacturers Association - Norm) or another recognized method.
- the above-mentioned object is achieved by the characterizing features of patent claim 1.
- the solution provides that in at least one channel the rings and disks each receive and position all the tubes of a channel by means of cylindrical recesses or bores, and the perimeter contour of the rings and the disks on the medium throughflow side in each case the centers of the outermost or innermost Follow tube bundle tubes, whereby the perimeter contour encompasses all of the outermost or innermost tubes.
- All tube bundle tubes are securely supported and positioned within the channel, all tubes are supported in such a way that the frequency of the first harmonic oscillation of the tubes is definitely above the excitation frequency of the tubes due to the medium flow and consequently there is no vibration resonance at the tube bundle tubes, Despite the smaller support spacing of the individual pipes, the medium pressure loss is increased only insignificantly, if at all.
- the width of the leg remains at least partially constant as a distance between the outer wall of the tube and the perimeter contour. This means that the same distance prevails between the center point or the outer wall of the outermost or innermost tubes to the perimeter contour, which simplifies the design side and the manufacturing side.
- the width of the leg is between 3 and 10 millimeters. This configuration ensures that not only inner or central tubes of the tube bundle are securely received and positioned, but also the outermost or innermost tubes of the respective channel. In a particularly advantageous embodiment, the width of the leg is less than 3 millimeters. With this configuration, a maximum of free Flow cross section of the heating or cooling medium can be achieved on the flow side of the rings or disks.
- the rings and disks formed with a perimeter contour are advantageously arranged in the outer channel or in the outer channels.
- the tubes of the respective tube bundle can be designed as U-tubes or as straight tubes.
- heat exchangers according to the invention can be equipped with differently configured tube bundles and can thus be used for a wide variety of applications.
- the tubes are arranged on the cross-sectional side within the channel in a triangular or quadrangular or other geometric division or structure.
- the triangular division or structure is particularly advantageous at high pressures in the heat exchanger, since a tube plate which is stiffened to a significantly higher degree can be achieved in this way.
- Square or other geometric structures or pipe divisions are advantageous for medium and low pressures.
- FIG. 1 shows a longitudinal section through a tube bundle heat exchanger according to a prior art
- FIG. 3 shows a partial cross section according to section A-A in FIG. 2,
- FIG. 4 shows a partial cross section according to section B-B in FIG. 2,
- FIG. 5 shows an enlarged detail view C according to FIG. 3,
- FIG. 6 shows an enlarged detail view D according to FIG. 3,
- tube bundle tubes are laid within the channel with a different (quadrangular) geometric structure
- 8 like FIG. 3 but tube bundle tubes are laid within the channel with a different (triangular) geometric structure
- FIG. 9 is an enlarged detail view E according to FIG. 8.
- a tube bundle heat exchanger 1 according to a prior art can be seen from FIG. 1.
- Such tube bundle heat exchangers are required for a wide variety of chemical and petrochemical processes.
- a heating or cooling medium 20, in most cases a heating gas, is fed through an inlet duct 18 to one or more ducts or gas ducts 4, 5 in which the heat or cold is directed to pipes or heating surface pipes 3 running therein
- Larger number of tube bundles 2 is released, which heats or cools a liquid or gaseous medium to be heated or cooled, for example water and / or steam.
- the structure of the tube bundle heat exchanger 1 according to FIG. 1 provides that the first gas duct or gas duct 4, the second gas duct or gas duct 5 and then the outlet duct 19 are connected concentrically to one another around the centrally arranged inlet duct 18.
- the channels 4, 5, 1 8, 1 9 have a common longitudinal axis 6, which corresponds to the longitudinal axis of the tube bundle heat exchanger 1.
- the cross section of the inlet channel 18 is preferably essentially round and that of the gas channels 4 and 5 and of the outlet channel 19 is essentially circular.
- the heating or cooling medium flow 20 flowing in at one end of the tube bundle heat exchanger 1 through the inlet channel 18 is deflected at the other end by the tube or end plate 17 receiving the tube bundle 2 by 180 ° and fed to the first gas channel or gas train 4. After flowing through the first gas channel 4, a further 180 ° deflection and supply of the heating or Cooling medium flow 20 in the second G ⁇ sk ⁇ n ⁇ l 5. Finally, the heating or cooling medium flow 20 after flow through the second gas channel 5 through the tube plate 17 7 is deflected again by 180 ° and discharged through the outlet channel 19 from the heat exchanger 1.
- heating or cooling medium 20 In order to increase the efficiency of the heat or cold transfer between heating or cooling medium 20 and the medium circulating in the tubes 3 and to be heated or cooled within the gas channels 4, 5 and to support the tubes 3 of the tube bundle 2, support or position the pipes 3 at certain intervals by means of deflection plates. It is thereby achieved that the heating or cooling medium flow 20 does not flow parallel to the tubes 3 through the gas duct 4, 5, but rather flows across the tubes 3 transversely or essentially transversely and thus a significantly better heat transfer is achieved.
- the baffle plates are designed in such a way that on the two jacket walls 7, 8 (inner 7 and outer 8 gas channel boundary) of the gas channel 4, 5 rings 9 or disks 10 are arranged alternately, so that a zigzag-shaped flow of heating or cooling medium flows through of the gas channel 4, 5 is formed.
- the outer tubes 3 of the tube bundle tubes running in the gas channel 4, 5 are supported and positioned by the rings 9 fastened to the jacket wall 8 and the inner tubes 3 of the tube bundle tubes extending in the gas channel 4, 5 by the disks 10 attached to the jacket wall 7.
- the tubes 3 are supported by the rings 9 or disks 10 in the axial direction each with a support distance S (distance between two rings 9 or between two disks 10), the support of the disks 10, viewed axially, in the middle between the support of the Rings 9 lies.
- the tube bundle heat exchanger 1 has at least one gas channel 4, 5 rings 9 and disks 10, each of which has all the tubes 3 of the tube bundle tubes of this gas channel 4, 5 by means of a cylindrical tube Pick up or position recess or hole 1 1. Furthermore, according to the invention, the perimeter contour 12 of the rings 9 and the disks 10 on the medium Flow-through side 13 each follow the center points 14, 15 of the outermost or innermost tube bundle tubes 3, the perimeter contour 12 comprising a leg 16 enveloping all outermost and innermost tubes 3.
- the medium throughflow side 13 of the rings 9 or the disks 10 is the side 13 of the rings 9 or disks 10 which is passed by the medium stream 20 and thus the free passage or passage of the heating or cooling medium stream 20 forms between ring 9 and inner jacket wall 7 or disk 10 and outer jacket wall 8, see FIGS. 3 to 9.
- the perimeter contour 12 of the rings 9 or disks 10 on the flow-through side 13 is not circular, but instead follows the centers 14, 15 of the outermost or innermost tube bundle tubes 3, as described above, i.e. the perimeter contour 12 of the rings 9 the center points 15 of the innermost and the perimeter contour 12 of the disks 10 the center points 14 of the outermost tube bundle tubes 3, the perimeter contour 12 also including ring or disc material or a leg 16 so that each individual tube bundle tube 3 is fringed or surrounded by this leg 1 6 (see FIGS. 3 to 9), so that the innermost or outermost tubes 3 are also laterally securely supported.
- the flow cross section on the flow-through side 13 of the baffle plates i.e.
- the width B of the material protrusion or leg 16 between the outer wall of the outermost or innermost tube 3 and the perimeter contour 12 remains at least partially preferably constant.
- Another preferred embodiment provides a width B of the leg 16 of three to ten millimeters, a particularly preferred embodiment provides a width B of the leg 16 of less than three millimeters.
- FIGS. 7 to 9 show a further advantageous embodiment of the invention, which consists in the perimeter contour 12 running at least partially parallel to an imaginary connecting line between two or more outer or inner tube centers 14, 15.
- the width B of the leg 16 is defined as the vertical distance between the perimeter contour 12 and the outer wall of the tube 3.
- the rings 9 and disks 10 according to the invention can be simplified and inexpensively manufactured on the production side and, on the other hand, the free passage cross section of the heater can be produced - or cooling medium 20 can be maximized on the flow side 13 of the rings 9 or discs 10.
- the bores or cylindrical recesses 1 1, with which the rings 9 and the disks 10 are formed for receiving all the tubes 3 of a gas channel 4, 5, are arranged in such a way that each individual tube bundle tube 3 is axially parallel to the longitudinal axis of the channel or tube bundle heat exchanger ⁇ are aligned and guided in the respective bores 1 1 of the rings 9 and disks 10.
- the tubes 3 are not firmly connected to one another with the rings 9 or disks 10 and can expand axially freely in the bores 11 when heated in the operating state.
- the rings 9 and disks 10 each receive all tube bundle tubes 3 of a channel or gas channel 4, 5, the former span S of each tube 3 between two rings 9 or between two disks 10 is halved to half the span S / 2.
- this is advantageous for the lateral support of the tube bundle tubes 3, since each individual tube 3 is supported twice as often as in known designs.
- the design of the invention advantageous in terms of preventing resonant vibrations of the tubes 3 and, consequently, the prevention of 1 to high mechanical stresses of these pipes 3 which are caused by the resonant vibrations.
- a vibration resonance is formed on the tubes 3 when the natural frequency of the tubes corresponds to the excitation vibration frequency of the medium or the heating or cooling medium flow 20, the excitation vibration frequency of the medium being dependent on the cross component of the flow velocity of the medium and the tube pitch while the natural frequency of the tubes 3 is mainly determined by the tube diameter, the wall thickness of the tubes 3 and the distance between the support points (tube plate 17, rings 9 and washers 10).
- the arrangement according to the invention allows the vibration resonance within the tube bundle heat exchanger 1 to be prevented in a simple manner and the tubes 3 to be securely supported without the distances between the deflection plates, i.e. to reduce the rings 9 and disks 10 with each other and thus to generate higher pressure losses on the channel or heating or cooling medium side 20.
- the halved support spacing may make it possible, without losing the advantageous effect, to increase the dimension of the support spacing or to reduce the wall thickness of the tubes 3.
- FIGS. 2 to 4 show a tube bundle heat exchanger 1 according to the invention, which is designed with two channels or gas channels 4, 5 arranged concentrically to one another in a preferred embodiment.
- the rings 9 and disks 10 formed with the perimeter contour 12 and receiving all the tubes 3 are advantageously arranged in the outer channel 5 or the outer gas channels. This measure prevents a high medium pressure loss within the heat exchanger 1, since the medium flow 20 in the inner channel 4, in which the gas is still at a very high temperature and consequently has a large volume or a high passage speed, allows a free passage, ie one larger flow area, finds. While FIGS.
- FIGS. 7 to 9 show a tube bundle heat exchanger 1 according to the invention with straight lines Tubes 3 formed tube bundle 2.
- the straight tubes 3 can be arranged on the cross-sectional side within the channel 4, 5 in a triangular or quadrangular or other geometric structure or tube division.
- a triangular pipe division as shown in FIGS. 8 and 9, is suitable for shell-and-tube heat exchangers 1 with high to very high pressures, while square-shaped pipe divisions according to FIG. 7 or another geometric pipe division is suitable for medium and low pressures.
- tube bundle heat exchangers 1 with tube bundles 2 formed from straight tubes 3 it may be advantageous to design rings 9 and / or disks 10 in the shape of a crescent moon (not shown). This leads to a stronger cross-flow of the tubes 3 by the heating or cooling medium flow 20 and thus also to a higher heat transfer.
- the tube bundle heat exchanger 1 according to the invention is not limited to the application examples listed in the aforementioned figures.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Lubricants (AREA)
- Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10333463.7A DE10333463C5 (de) | 2003-07-22 | 2003-07-22 | Rohrbündelwärmetauscher |
PCT/DE2004/001439 WO2005010450A1 (de) | 2003-07-22 | 2004-07-06 | Rohrbündelwärmetauscher |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1646836A1 true EP1646836A1 (de) | 2006-04-19 |
EP1646836B1 EP1646836B1 (de) | 2006-11-08 |
Family
ID=34071845
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04738868A Not-in-force EP1646836B1 (de) | 2003-07-22 | 2004-07-06 | Rohrbündelwärmetauscher |
Country Status (9)
Country | Link |
---|---|
US (1) | US20070181292A1 (de) |
EP (1) | EP1646836B1 (de) |
JP (1) | JP4573183B2 (de) |
KR (1) | KR100751961B1 (de) |
AT (1) | ATE344911T1 (de) |
CA (1) | CA2532466C (de) |
DE (2) | DE10333463C5 (de) |
DK (1) | DK1646836T3 (de) |
WO (1) | WO2005010450A1 (de) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007083927A1 (en) * | 2006-01-18 | 2007-07-26 | Lg Chem, Ltd. | Reactor with improved heat transfer performance |
US20130292089A1 (en) * | 2012-05-01 | 2013-11-07 | Norcross Corporation | Dual passage concentric tube heat exchanger for cooling/heating of fluid in a low pressure system |
US20140014294A1 (en) * | 2012-07-13 | 2014-01-16 | Areva Np Inc. | U-Bend Tube Compression/Distortion Stabilization System (CDSS) |
EP3115734A1 (de) * | 2015-07-06 | 2017-01-11 | Casale SA | Rohrbündelausrüstung mit schwingungsdämpfenden sperren und zugehöriges montageverfahren |
ES2842423T3 (es) | 2017-05-26 | 2021-07-14 | Alfa Laval Olmi S P A | Intercambiador de calor de carcasa y tubos |
US11920878B2 (en) * | 2017-08-28 | 2024-03-05 | Watlow Electric Manufacturing Company | Continuous helical baffle heat exchanger |
US11913736B2 (en) * | 2017-08-28 | 2024-02-27 | Watlow Electric Manufacturing Company | Continuous helical baffle heat exchanger |
EP3676554B1 (de) * | 2017-08-28 | 2023-06-14 | Watlow Electric Manufacturing Company | Kontinuierlicher schraubenförmiger umlenkwärmetauscher |
Family Cites Families (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2774575A (en) * | 1952-03-07 | 1956-12-18 | Worthington Corp | Regenerator |
US2873098A (en) * | 1955-10-03 | 1959-02-10 | Yates American Machine Co | Heat exchange apparatus |
US3240267A (en) * | 1963-07-16 | 1966-03-15 | Borg Warner | Heat exchanger |
US3475137A (en) * | 1967-03-09 | 1969-10-28 | Chemical Construction Corp | Apparatus for exothermic catalytic reactions with integral heat exchanger |
US3490521A (en) * | 1968-03-12 | 1970-01-20 | Westinghouse Electric Corp | Tube and shell heat exchanger |
US3802498A (en) * | 1970-02-02 | 1974-04-09 | N Romanos | Shell and tube heat exchanger with central conduit |
US3827484A (en) * | 1970-02-04 | 1974-08-06 | W Wolowodiuk | Liquid metal heat exchanger |
US3656548A (en) * | 1970-04-23 | 1972-04-18 | Borg Warner | Self-positioning baffle for shell and tube heat exchangers |
US3741164A (en) * | 1971-03-03 | 1973-06-26 | Foster Wheeler Corp | Sodium heated steam generator |
FR2233587A1 (en) * | 1973-06-14 | 1975-01-10 | Chausson Usines Sa | Tube bundle heat exchanger - has tube ends shaped as complementary polygons |
JPS5424353A (en) * | 1977-07-27 | 1979-02-23 | Mitsubishi Heavy Ind Ltd | Multiple heat exchanger |
CH630721A5 (de) * | 1978-01-23 | 1982-06-30 | Agresto Ag International Sa | Rohrbuendelwaermeaustauscher mit stroemungsleitvorrichtung. |
CA1122202A (en) * | 1979-11-23 | 1982-04-20 | Gordon M. Cameron | Heat exchanger having improved tube layout |
JPS56162400A (en) * | 1980-05-19 | 1981-12-14 | Toshiba Corp | U-tube type heat exchanger |
EP0044734B1 (de) * | 1980-07-23 | 1985-02-20 | Armstrong Engineering Limited | Wärmetauscher |
JPS6284299A (ja) * | 1985-10-04 | 1987-04-17 | Yanmar Diesel Engine Co Ltd | 多管式熱交換器 |
US4834173A (en) * | 1987-11-20 | 1989-05-30 | American Standard Inc. | Pressure actuated baffle seal |
EP0382098B2 (de) * | 1989-02-10 | 1997-01-02 | Mitsubishi Jukogyo Kabushiki Kaisha | Mehrrohrtypwärmetauscher |
DE4130693C1 (de) * | 1991-09-14 | 1992-10-29 | Erno Raumfahrttechnik Gmbh, 2800 Bremen, De | |
US5615738A (en) * | 1994-06-29 | 1997-04-01 | Cecebe Technologies Inc. | Internal bypass valve for a heat exchanger |
US5653282A (en) * | 1995-07-19 | 1997-08-05 | The M. W. Kellogg Company | Shell and tube heat exchanger with impingement distributor |
US5660230A (en) * | 1995-09-27 | 1997-08-26 | Inter-City Products Corporation (Usa) | Heat exchanger fin with efficient material utilization |
JPH10227591A (ja) * | 1997-02-14 | 1998-08-25 | Usui Internatl Ind Co Ltd | Egrガス冷却装置 |
DE59705073D1 (de) * | 1997-03-14 | 2001-11-29 | Borsig Babcock Ag | Wärmetauscher mit U-Rohren |
US6142215A (en) * | 1998-08-14 | 2000-11-07 | Edg, Incorporated | Passive, thermocycling column heat-exchanger system |
-
2003
- 2003-07-22 DE DE10333463.7A patent/DE10333463C5/de not_active Expired - Fee Related
-
2004
- 2004-07-06 WO PCT/DE2004/001439 patent/WO2005010450A1/de active Application Filing
- 2004-07-06 JP JP2006522879A patent/JP4573183B2/ja active Active
- 2004-07-06 EP EP04738868A patent/EP1646836B1/de not_active Not-in-force
- 2004-07-06 DE DE502004001966T patent/DE502004001966D1/de active Active
- 2004-07-06 KR KR1020067001423A patent/KR100751961B1/ko active IP Right Grant
- 2004-07-06 US US10/565,305 patent/US20070181292A1/en not_active Abandoned
- 2004-07-06 DK DK04738868T patent/DK1646836T3/da active
- 2004-07-06 AT AT04738868T patent/ATE344911T1/de active
- 2004-07-06 CA CA002532466A patent/CA2532466C/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2005010450A1 * |
Also Published As
Publication number | Publication date |
---|---|
CA2532466C (en) | 2008-10-21 |
WO2005010450A1 (de) | 2005-02-03 |
DE10333463B4 (de) | 2006-05-04 |
CA2532466A1 (en) | 2005-02-03 |
KR100751961B1 (ko) | 2007-08-27 |
KR20060038456A (ko) | 2006-05-03 |
DK1646836T3 (da) | 2007-03-19 |
JP4573183B2 (ja) | 2010-11-04 |
DE502004001966D1 (de) | 2006-12-21 |
DE10333463A1 (de) | 2005-02-17 |
EP1646836B1 (de) | 2006-11-08 |
JP2006528762A (ja) | 2006-12-21 |
ATE344911T1 (de) | 2006-11-15 |
US20070181292A1 (en) | 2007-08-09 |
DE10333463C5 (de) | 2014-04-24 |
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