EP1305561A1 - Vorrichtung zur wärmeübertragung - Google Patents
Vorrichtung zur wärmeübertragungInfo
- Publication number
- EP1305561A1 EP1305561A1 EP01951364A EP01951364A EP1305561A1 EP 1305561 A1 EP1305561 A1 EP 1305561A1 EP 01951364 A EP01951364 A EP 01951364A EP 01951364 A EP01951364 A EP 01951364A EP 1305561 A1 EP1305561 A1 EP 1305561A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat transfer
- fluid
- support element
- heat
- channels
- 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
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
- 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
-
- 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
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
- F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium
-
- 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
- F28D9/005—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 the plates having openings therein for both heat-exchange media
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2225/00—Reinforcing means
- F28F2225/08—Reinforcing means for header boxes
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S165/00—Heat exchange
- Y10S165/906—Reinforcement
Definitions
- the invention relates to a device for heat transfer from a first fluid to a second fluid separated from the first fluid with a stack-like or shell-like structure comprising at least two layers, in particular plates, according to the preamble of claim 1.
- heat exchangers with a first channel through which a high-pressure refrigerant flows and a second channel through which low-pressure refrigerant flows and separated from the first channel are provided in a C0 2 vehicle air conditioning system.
- a so-called internal or internal heat exchanger is provided.
- the internal heat exchanger is flowed through by the refrigerant (C0 2 ) in the counterflow principle or in the cocurrent principle.
- the fluids flow through the heat exchanger once on the way from the gas cooler to the evaporator and the second time between the evaporator and the compressor.
- the main task of the internal heat exchanger is to additionally cool the refrigerant before expansion.
- the heat is transferred from the high pressure side to the gas cooler Low pressure side delivered after the evaporator (before entering the compressor).
- the partially still liquid refrigerant evaporates completely before it reaches the compressor.
- Heat exchangers are already known which are manufactured in a comparatively compact manner in order to reduce mass and volume.
- so-called micro heat exchangers are provided, for example. These consist in particular of structured plates that are stacked on top of one another and either soldered, screwed or connected accordingly. Correspondingly provided channels of the heat exchanger are also sealed at the same time. The fluids, which come into thermal contact with one another in the heat exchanger, are conducted via the channels between the plates.
- the fluids are led into the individual layers through inlet openings or outlet openings, so that a heat-absorbing and a heat-emitting fluid flows alternately in different layers.
- the distribution or the merging of the fluids to or from the individual channels takes place in the entry or exit area.
- the respective fluid flow splits or collects in these areas.
- the large pressurized area in the area of the free cross-section leads to large material stresses, which leads to material deformation, e.g. B. flow, or failure of the component.
- the object of the invention is to propose a device for heat transfer which, with a small volume, realizes a comparatively large heat-transfer surface and thereby ensures trouble-free operation even at large different pressure levels of the two fluids.
- a device is characterized in that the entry and / or exit area comprises at least one support element.
- the resulting free cross-section and in particular the bending moment that occurs in the entry or exit area are substantially reduced as a result. This ensures that the surface under pressure, in particular on the side operated with comparatively low pressure, is supported and is therefore disadvantageous Deformation of the plate is prevented.
- a support element according to the invention provided on each plate can transmit corresponding pressure forces from plate to plate until a comparatively massive cover plate absorbs the pressure forces, so that deformation of the plates or failure of the entire component is effectively prevented.
- numerous support elements are provided both in the entry and in the exit area, so that both the resulting free cross sections and the bending stresses that occur are further reduced.
- this advantageously has a comparatively large number of support elements on the side facing the heat transfer area.
- comparatively few support elements are provided on the side of the entry area facing the entry opening. The corresponding is advantageously transferred to the exit area.
- the heat exchanger according to the invention can have much thinner-walled plates in comparison to the prior art with the same pressure differences between the two fluids, which can preferably lead to a significant reduction in mass and volume of the entire heat exchanger, given the heat output to be transferred.
- the support elements advantageously increase the heat-transferring surface, so that the heat transfer of the heat exchanger according to the invention is additionally improved. This means that, given the heat output to be transferred, the volume of a heat exchanger according to the invention can be additionally reduced.
- the length of the support element is designed as a multiple of its width. This ensures that the support element, for example with a comparable flow resistance, has a substantially greater support effect and heat-transferring surface.
- the heat exchanger can hereby advantageously be subjected to a greater pressure difference between the two fluid streams without disadvantageous material deformation or failure of the heat exchanger.
- the support element is advantageously designed as a fluid guide element. This enables an improved fluid flow to be generated by means of the support elements according to the invention.
- the fluid is distributed uniformly over the channels of the heat transfer region by means of support elements according to the invention or is merged from the channels in a flow-favorable manner and passed on to a corresponding collecting channel. With this, a more evenly distributed loading of the channel structure of the heat transfer area can be implemented, which in turn leads to an improved heat transfer of the heat exchanger.
- two adjacent support elements with an angle of less than 20 °, preferably between 10 ° and 15 °, are arranged relative to one another.
- the opening angle of the fluid flow the so-called In contrast, the diffuser angle according to the prior art is frequently over 50 °.
- a comparatively small opening angle according to the invention between two adjacent support elements prevents, for example, separation of the fluid flow in the entry or exit area, so that disadvantageous energy losses are minimized and, at the same time, uneven loading of the channel structure of the heat transfer area can be prevented.
- the Reynolds number which is dependent on the prevailing flow conditions and is dependent on the opening angle, the fluid pressure and the arrangement or configuration of the support elements or the channels of the heat transfer area, is also of crucial importance.
- the side wall of the support element is straight and / or curved.
- the design of a support element as a polygon is also conceivable.
- the support elements are preferably constructed in terms of materials and geometry in such a way that they achieve the greatest possible support effect and a very good flow distribution with a comparatively low loss of flow pressure. If appropriate, elongated support elements can advantageously have widened sections to improve the support effect and the flow guidance.
- At least one support element is designed as an extension of a partition between two channels of the heat transfer area. This makes it possible, for example, to implement the channels of the heat transfer region in a much more uniform manner.
- a further improvement of the flow control can be implemented.
- a Support element formed as an extension of the channel partition a curved transition from the support element to the channel partition is preferably provided.
- a curved transition can lead to an advantageous fluid flow, so that disadvantageous pressure losses can be minimized.
- the support element have a curved side wall, but the channel partition wall can also have a curved side wall, at least in the edge region, so that a more favorable fluid flow can be generated.
- a transition with a slight bend, which has a comparatively small kink, can also be realized here.
- the various layers of the stack-like or shell-shaped device are preferably designed as flat or curved plates or as cylindrical components which can be stacked one inside the other due to different diameters, so that advantageous production of the heat exchanger according to the invention can be realized.
- cover plates closing the heat exchanger are preferably provided.
- the design and arrangement of the support elements are adapted to the channels of the heat transfer area.
- the channels and the support elements are produced on or in the layers by means of a removal or coating manufacturing process, so that the support elements and the channels can be produced comparatively small.
- Corresponding recesses in the plates are preferably produced by means of a photolithographic structuring process with a subsequent etching process, so that, if appropriate, all process steps both for producing the channels of the heat transfer region and for producing the support elements in the entry and exit regions in each case one step can be implemented.
- the heat exchanger is formed by plates stacked one on top of the other and soldered to one another, in which at least some of the corresponding recesses are provided, for example for forming the channels or support elements. At least one solder layer can be provided between the plates for a soldering process.
- the soldering process is advantageously carried out in a vacuum or in an inert gas atmosphere.
- the plates are preferably stacked one above the other with at least one intermediate solder layer in the later arrangement of the component and pressed in particular in the cold state, even before the soldering process. By pressing the plates before the actual soldering process, the plates are not pressed firmly at comparatively high temperatures. This eliminates the need for comparatively complex pressing tools that would have to withstand the high soldering temperatures.
- FIG. 1 shows a schematic representation of the structural and flow conditions of a heat exchanger according to the prior art
- FIG. 2 shows a schematically illustrated free cross section by overlapping two layers according to the prior art
- FIG. 3 shows a schematically illustrated, reduced free cross section according to the invention with straight support elements
- Figure 4 is a schematically illustrated entry or exit area according to the invention with reinforced support elements and
- FIG. 5 shows a schematically illustrated further entry or exit area with curved support elements.
- FIG. 1 A heat exchanger according to the prior art is shown in FIG.
- the heat exchanger comprises individual plates 1, 2, 3 for heat transmission, which are soldered or welded together, packed between two cover plates 8, 9 and provided with small channels 11, 12, 13 and flow openings 4, 5, 6, 7.
- C0 2 low pressure (arrow FEI) flows into an inlet opening 15 of the cover plate 8, through the channels 11 of the Heat transfer plate 1 from bottom to top, further through the flow opening 5 of the heat transfer plate 2 through to the heat transfer plate 3 and there also through its small channels from bottom to top and through the corresponding flow openings 7 of the heat transfer plates 3, 2, 1 and then through the outlet opening 17 Cover plate 8 off (arrow FA1).
- the heat exchanger shown is flowed through by the high-pressure side refrigerant (black arrows) in a first direction and in countercurrent by the low-pressure side refrigerant (hatched arrows).
- the heat exchanger shown in Figure 1 has only three heat transfer plates 1, 2, 3, due to a more advantageous representation. This consists of individual layers defined by the heat transfer plates 1, 2, 3, which are in counterflow from the C0 2 , which is on one side at high pressure (up to approximately 150 bar) at high temperature and on the other side at low pressure ( up to approximately 60 bar) and at a low temperature.
- the heat transfer coefficient on the low pressure side is generally much smaller than that on the high pressure side.
- the basic aim should therefore be that the product of the heat transfer coefficient and the heat transfer surface on the high pressure side be the product
- Heat transfer coefficient and heat transfer area on the low pressure side is adjusted.
- the compact heat exchanger shown which consists of individual profiles, ie the heat transfer plates 1, 2, 3, into which the small channels 11, 12, 13 are incorporated, by appropriate adjustment of the hydraulic diameter of the small channels 11, 12, 13.
- a heat exchanger according to the invention can advantageously be produced from copper and copper alloy, stainless steel, aluminum and other materials.
- a heat exchanger according to the invention can advantageously be used as the inner heat exchanger of a C0 2 -lima system in vehicles, in particular motor vehicles.
- the first (high pressure) flow channel marked by black arrows in FIG. 1 lies in a first flow path from a gas cooler to an evaporator and the second (low pressure) flow channel marked by hatched arrows in the figure lies in a second flow path from the evaporator to one Vehicle air conditioning compressor.
- a high pressure up to approximately 150 bar and a high temperature can prevail in the first flow path and a low pressure up to approximately 60 bar and a relatively low temperature in the second flow path.
- FIG. 2 schematically shows a free cross section 24, which arises, for example, by overlapping the inlet area E1 of the fluid I with the outlet area A2 of the fluid II according to the prior art.
- the free cross section 24 has a comparatively large area under pressure and therefore has to absorb comparatively large material stresses, which can lead to deformations, in particular of the plates 2, 3, and to failure of the heat exchanger.
- FIG. 3 shows a section of the two plates 2, 3 corresponding to the section of FIG. 2.
- the entry or exit area of the plates 2, 3 according to the invention has support elements 18 according to the invention.
- the support elements 18 according to FIG. 3 are designed as rectilinear support elements 18.
- some support elements 18 ' are formed as an extension of a duct partition 19.
- an opening angle ⁇ which is formed from two adjacent support elements 18, is substantially smaller than an opening angle ⁇ without support elements 18 according to the prior art according to the invention.
- the structuring by means of the support elements 18 thus distributes the flow of the fluids more evenly over the channels of the heat transfer area and the opening angle is reduced, for example, from approximately 50 ° to approximately 10 ° to 15 °.
- this has the result that a detachment of the fluid flow, which entails energy losses and an uneven loading of the channel structure 11, 12, 13, is largely prevented.
- the prevention of detachment and thus the reduction of energy losses essentially depends on the Reynolds number. This in turn depends, among other things, on the opening angle and also on the set pressures of the fluids.
- FIG. 3 illustrates that the reduced free cross section 23 compared to the free cross section 24 of FIG. 2 significantly reduces the pressurized pressure Represents area and thus significantly reduces the bending stresses that occur. This largely prevents deformation of the plates 1, 2, 3 or failure of the heat exchanger.
- FIG. 4 shows, in particular, support elements 18 which have local reinforcements 20 to reinforce the support effect according to the invention.
- FIG. 5 shows support elements 18 which have a curved side wall.
- This inventive design of the support elements 18 leads in particular to an advantageous flow guidance and distribution of the fluids to the channels 11, 12, 13.
- the curved support elements 18 shown in FIG. 5 have an angular transition 21.
- a curved transition 21, not shown in more detail, can lead to a further improvement in the flow guidance.
- a curved end region of the channel partition walls 19 can also be advantageous.
- the support elements 18 according to the invention distributed the occurring load much better, so that they have an additional load-bearing function. According to the prior art, inter alia, the occurring load had to be taken over predominantly from the edge regions of the plates 1, 2, 3, so that material can be advantageously saved in the edge regions, for example, with the aid of the support elements 18 according to the invention.
- the plates 1, 2, 3 are alternately flowed through by a heat-absorbing and a heat-emitting fluid in the countercurrent or in the cocurrent principle.
- a heat-absorbing and a heat-emitting fluid in the countercurrent or in the cocurrent principle.
- several, for. B. two adjacent plates 1, 2 are flowed through by the same fluid and only the subsequent plate 3 or several adjacent plates are flowed through by the other fluid.
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)
- Details Of Heat-Exchange And Heat-Transfer (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10035939 | 2000-07-21 | ||
DE10035939A DE10035939A1 (de) | 2000-07-21 | 2000-07-21 | Vorrichtung zur Wärmeübertragung |
PCT/DE2001/002162 WO2002008680A1 (de) | 2000-07-21 | 2001-06-09 | Vorrichtung zur wärmeübertragung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1305561A1 true EP1305561A1 (de) | 2003-05-02 |
EP1305561B1 EP1305561B1 (de) | 2005-09-21 |
Family
ID=7649985
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01951364A Expired - Lifetime EP1305561B1 (de) | 2000-07-21 | 2001-06-09 | Vorrichtung zur wärmeübertragung |
Country Status (8)
Country | Link |
---|---|
US (1) | US7040387B2 (de) |
EP (1) | EP1305561B1 (de) |
JP (1) | JP2004504584A (de) |
KR (1) | KR20020032602A (de) |
BR (1) | BR0106982A (de) |
DE (2) | DE10035939A1 (de) |
ES (1) | ES2248358T3 (de) |
WO (1) | WO2002008680A1 (de) |
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AU2003902200A0 (en) * | 2003-05-06 | 2003-05-22 | Meggitt (Uk) Ltd | Heat exchanger core |
CN1833153B (zh) * | 2003-08-01 | 2012-04-04 | 贝洱两合公司 | 热交换器及其制造方法 |
DE10352128A1 (de) * | 2003-11-04 | 2005-06-09 | Dylla, Anett, Dipl.-Ing. | Multifunktionales Energienetz und Vorrichtungen hierfür |
US7343965B2 (en) | 2004-01-20 | 2008-03-18 | Modine Manufacturing Company | Brazed plate high pressure heat exchanger |
SE526831C2 (sv) * | 2004-03-12 | 2005-11-08 | Alfa Laval Corp Ab | Värmeväxlarplatta och plattpaket |
JP4818044B2 (ja) * | 2006-09-28 | 2011-11-16 | 三洋電機株式会社 | 熱交換器の製造方法 |
SE533310C2 (sv) * | 2008-11-12 | 2010-08-24 | Alfa Laval Corp Ab | Värmeväxlarplatta och värmeväxlare innefattande värmeväxlarplattor |
JP5106453B2 (ja) * | 2009-03-18 | 2012-12-26 | 三菱電機株式会社 | プレート式熱交換器及び冷凍空調装置 |
DE102009043828B4 (de) * | 2009-08-21 | 2019-02-14 | Ttz Thermo Technik Zeesen Gmbh & Co. Kg | Plattenwärmeübertrager |
US9752836B2 (en) * | 2010-11-12 | 2017-09-05 | Mitsubishi Electric Corporation | Plate heat exchanger and heat pump apparatus |
US8869398B2 (en) | 2011-09-08 | 2014-10-28 | Thermo-Pur Technologies, LLC | System and method for manufacturing a heat exchanger |
CN104321611B (zh) * | 2012-05-11 | 2016-08-31 | 三菱电机株式会社 | 层叠型全热交换元件以及热交换换气装置 |
CN103759474B (zh) * | 2014-01-28 | 2018-01-02 | 丹佛斯微通道换热器(嘉兴)有限公司 | 板式换热器 |
EP3093602B1 (de) | 2015-05-11 | 2020-04-15 | Alfa Laval Corporate AB | Wärmetauscherplatte und plattenwärmetauscher |
WO2017019141A1 (en) * | 2015-07-24 | 2017-02-02 | Exxonmobil Upstream Research Company | Enhanced heat transfer in plate-fin heat exchangers |
EP3150952A1 (de) * | 2015-10-02 | 2017-04-05 | Alfa Laval Corporate AB | Wärmetauschplatte und plattenwärmetauscher |
US10914533B2 (en) * | 2017-03-24 | 2021-02-09 | Hanon Systems | Intercooler for improved durability |
RU177117U1 (ru) * | 2017-06-26 | 2018-02-08 | Общество с ограниченной ответственностью "Корпорация Акционерной Компании "Электросевкавмонтаж" | Пластина теплообменника пластинчатого |
EP3489604B1 (de) * | 2017-11-24 | 2020-12-23 | TitanX Holding AB | Fahrzeugkondensator |
US11486657B2 (en) * | 2018-07-17 | 2022-11-01 | Tranter, Inc. | Heat exchanger heat transfer plate |
PL3650795T3 (pl) * | 2018-11-07 | 2021-07-05 | Alfa Laval Corporate Ab | Płyta wymiennika ciepła |
KR102598408B1 (ko) * | 2018-12-06 | 2023-11-07 | 한온시스템 주식회사 | 열교환기 |
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JP3719453B2 (ja) * | 1995-12-20 | 2005-11-24 | 株式会社デンソー | 冷媒蒸発器 |
SE9700614D0 (sv) * | 1997-02-21 | 1997-02-21 | Alfa Laval Ab | Plattvärmeväxlare för tre värmeväxlande fluider |
DK174409B1 (da) * | 1998-01-12 | 2003-02-17 | Apv Heat Exchanger As | Varmevekslerplade med forstærket kantudformning |
JP3331950B2 (ja) * | 1998-02-27 | 2002-10-07 | ダイキン工業株式会社 | プレート型熱交換器 |
JP3292128B2 (ja) * | 1998-02-27 | 2002-06-17 | ダイキン工業株式会社 | プレート型熱交換器 |
SE514714C2 (sv) * | 1999-08-27 | 2001-04-09 | Alfa Laval Ab | Lödd plattvärmeväxlare med dubbelväggiga plattor utan inre anliggning mittför lödförbindningarna |
DE19948222C2 (de) * | 1999-10-07 | 2002-11-07 | Xcellsis Gmbh | Plattenwärmetauscher |
DE10021481A1 (de) * | 2000-05-03 | 2001-11-08 | Modine Mfg Co | Plattenwärmetauscher |
US6629561B2 (en) * | 2001-06-08 | 2003-10-07 | Visteon Global Technologies, Inc. | Module for a heat exchanger having improved thermal characteristics |
US6662561B1 (en) * | 2002-07-30 | 2003-12-16 | Robert Bosch Corporation | Means to dampen the effect of pressure oscillations on a control valve |
-
2000
- 2000-07-21 DE DE10035939A patent/DE10035939A1/de not_active Ceased
-
2001
- 2001-06-09 US US10/088,285 patent/US7040387B2/en not_active Expired - Fee Related
- 2001-06-09 EP EP01951364A patent/EP1305561B1/de not_active Expired - Lifetime
- 2001-06-09 KR KR1020027003652A patent/KR20020032602A/ko not_active Application Discontinuation
- 2001-06-09 BR BR0106982-9A patent/BR0106982A/pt not_active Application Discontinuation
- 2001-06-09 ES ES01951364T patent/ES2248358T3/es not_active Expired - Lifetime
- 2001-06-09 JP JP2002514326A patent/JP2004504584A/ja active Pending
- 2001-06-09 WO PCT/DE2001/002162 patent/WO2002008680A1/de active IP Right Grant
- 2001-06-09 DE DE50107511T patent/DE50107511D1/de not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
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See references of WO0208680A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2002008680A1 (de) | 2002-01-31 |
KR20020032602A (ko) | 2002-05-03 |
EP1305561B1 (de) | 2005-09-21 |
DE50107511D1 (de) | 2005-10-27 |
BR0106982A (pt) | 2002-05-14 |
US7040387B2 (en) | 2006-05-09 |
JP2004504584A (ja) | 2004-02-12 |
DE10035939A1 (de) | 2002-02-07 |
US20030094271A1 (en) | 2003-05-22 |
ES2248358T3 (es) | 2006-03-16 |
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