EP0911156A1 - Arrangement pour tempérer dans une machine d'impression - Google Patents

Arrangement pour tempérer dans une machine d'impression Download PDF

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Publication number
EP0911156A1
EP0911156A1 EP98109590A EP98109590A EP0911156A1 EP 0911156 A1 EP0911156 A1 EP 0911156A1 EP 98109590 A EP98109590 A EP 98109590A EP 98109590 A EP98109590 A EP 98109590A EP 0911156 A1 EP0911156 A1 EP 0911156A1
Authority
EP
European Patent Office
Prior art keywords
dampening solution
circulation system
coolant
temperature control
circulation
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
EP98109590A
Other languages
German (de)
English (en)
Other versions
EP0911156B1 (fr
Inventor
Martin Prummer
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.)
t e c h n o trans AG
Original Assignee
t e c h n o trans 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
Application filed by t e c h n o trans AG filed Critical t e c h n o trans AG
Publication of EP0911156A1 publication Critical patent/EP0911156A1/fr
Application granted granted Critical
Publication of EP0911156B1 publication Critical patent/EP0911156B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/22—Means for cooling or heating forme or impression cylinders
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F7/00—Rotary lithographic machines
    • B41F7/20—Details
    • B41F7/24—Damping devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • 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
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0077—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for tempering, e.g. with cooling or heating circuits for temperature control of elements

Definitions

  • the invention relates to a temperature control arrangement for Temperature control of a dampening solution and / or selected rollers a printing press according to the preamble of claim 1.
  • the invention has for its object a Tempering arrangement to create that in less expensive Made way and for different heat exchange functions can be set up.
  • a changeover from one heat exchange function to another under otherwise unchanged structure of the temperature control arrangement may be possible.
  • a essential feature of the invention Temperature control arrangement is the provision of a single one Three-media heat exchange device instead of several separate heat exchangers. This enables the Fluid all circulation systems in different to bring heat exchange relationship to each other so that a Variety of heat exchange functions can be realized. As a result, the invention can easily be applied to different ones Customize use cases. Despite the high flexibility and Customizability are those for providing the invention required costs lower than for plants of the known Kind, since a three-media heat exchange device according to the Invention only slightly more expensive than a single one conventional heat exchanger needs to be. Furthermore, the Basic structure of the tempering arrangement for various Heat exchange functions cannot be changed. It is only a retrofit of the only three-media heat exchange device required. All you need is her distribution device designed for a heat exchange function by another distribution device at otherwise unchanged basic structure of the heat exchange device be converted. Advantageous developments of the invention are listed in the subclaims.
  • a temperature control arrangement comprises a dampening solution circulation system U I , a coolant circulation system U II and a refrigerant circulation system U III .
  • the dampening solution circulation system U I is designed as an open system and contains a buffer memory 30 for storing a suitable amount of dampening solution.
  • a pump 34 and a temperature sensor 35 are provided one behind the other at a point downstream of the buffer store 30.
  • a line 33 branches off from the main circuit on the downstream side of the temperature sensor 35 in order to lead a partial quantity of the dampening solution circulating in the main circuit U I to a storage container 32 of a dampening solution application device.
  • the dampening solution can flow back from the storage container 32 into the buffer container 30 via a line 31.
  • Suitable devices for example in the form of a throttle 35, are provided in the branch line 33 to ensure that the branched-off amount of dampening solution is always smaller than the amount that circulates in the main circuit.
  • the dampening solution circulating in the circulation system U I is also passed through a three-medium heat exchange device which bears the general reference number 1 in FIG. 1 and which will be discussed in more detail below.
  • the coolant circulation system U II which is preferably designed as a closed system, contains a control valve 40 and a pump 41 on the upstream side of a roller cooling device (not shown) and a temperature sensor 42 on the downstream side of the roller cooling device.
  • the coolant circulating in the circulation system U II is likewise passed through the three-medium heat exchange device 1 .
  • a bypass line 43 is provided on the downstream side of the control valve 40 and contains a flow restriction throttle 44 and a heating device 45.
  • the refrigerant circulation system U III is part of a refrigeration device which, in a manner known per se, consists of at least one compressor 20, a condenser 21, a collecting container 22, a control valve 23, preferably in the form of a solenoid valve, a dryer 24, a sight glass 25 and an expansion valve 26.
  • the three-medium heat exchange device 1 is supplied with refrigerant by integrating it into the refrigerant circulation system U III like the other two circulation systems U I and U II .
  • the refrigerant circulation system U III is designed as a closed system.
  • a control device 50 is provided in order to operate each such system independently or jointly by switching the pumps 34 or 41 of the dampening solution or coolant circulation system U I or U II on and with cooling energy from the refrigerant.
  • To supply circulation system U III depending on the heat exchange function in which the three-media heat exchange device 1 is operated, which will be discussed in more detail below.
  • the control device 50 also controls the operation of the refrigerant circulation system U III and can monitor the temperature of the dampening solution and coolant circulation system U I and U II .
  • top and bottom refer to the location the structural parts of the heat exchange device 1, as in the Drawing is shown.
  • the invention is based on a such position of use of the heat exchange device 1 is not limited.
  • the heat exchange device 1 can preferably be designed in the form of a plate exchanger, consisting of a multiplicity of plates 2 arranged side by side in succession, for example plates 2 1 , 2 2 , 2 3 ... 2 n , in whose respective surfaces complementary grooves or grooves are made, so that flow channels 10, in particular 10 1 , 10 2 , 10 3 ... 10 n , each with an inlet and an outlet end, are formed after assembly between adjacent plate surfaces, cf. e.g. Figures 4A and 4B.
  • a fluid for example water, can be introduced into a relevant flow channel 10 via a distributor device and can be discharged to the outside again after flowing through the flow channel 10.
  • the flow channels 10 are hermetically sealed from one another and can each be distributed in a meandering manner or in some other suitable manner over the plate surfaces.
  • the distributor device comprises a two-chamber distributor arrangement 3 for the separate supply and discharge of the dampening solution or coolant originating from the circulation systems U I and U II , and a single-chamber distributor arrangement 6 for the supply and discharge of the refrigerant from the circulation system U III , in each case into the relevant flow channels 10.
  • Each two-chamber distributor arrangement and single-chamber distributor arrangement 3, 6 comprises a distributor pipe near the upper ends of the flow channels 10 and a distributor pipe near their lower ends.
  • the distributor pipes penetrate the plate exchanger axially and are accommodated in the plates 2 in receiving bores that are aligned with one another. They also preferably extend parallel to one another.
  • Each distributor pipe of the two-chamber distributor arrangement 3 comprises an upper longitudinal chamber 4 and a lower longitudinal chamber 5, which are hermetically sealed from one another by an intermediate partition wall.
  • the upper chamber 4 has an open and a closed axial end 4a and 4b, and likewise the lower chamber 5 has an open and a closed axial end 5a and 5b.
  • An open axial end 4a of the upper chamber 4 is adjacent to a closed axial end 5b of the lower chamber 5, and conversely a closed axial end 4b of the upper chamber 4 is adjacent to an open axial end 5a of the lower chamber 5.
  • This arrangement facilitates the connection of the relevant manifold to the respective circulation system U I , U II , U III .
  • the single chamber manifold assembly 6 includes, as shown in FIG. 4B shows, an upper and a lower simple manifold each with an open axial end 6a for supply and discharge of the refrigerant and an opposing closed one axial end.
  • each manifold of the two-chamber manifold assembly 3 are at selected axial distances from each other Openings 7, 8 which the interior of the concerned Chamber 4 or 5 with selected flow channels 10 connect so that only the selected flow channels 10 be charged with the fluid that in the relevant chamber 4 or 5 was introduced.
  • each manifold of the single chamber manifold assembly 6 at selected axial intervals from each other openings 9 are provided around the in the single chamber manifold assembly 6 introduced refrigerants in selected Forward flow channels 10. This can be achieved be that adjacent flow channels 10 with different fluids are applied and they come into heat transfer relationship with each other.
  • the first heat exchange function is shown in FIGS. 4A and 4B and is characterized in that the refrigerant flows through the single-chamber distributor arrangement 6 connected to the circulation system U III and the openings 9 formed therein into the sequence of flow channels 10 2 , 10 6 , 10 10 , 10 14 , etc. are introduced, which are indicated in FIGS. 4A and 4B by cross-dashed lines.
  • Each upper and lower distributor pipe consequently has openings 9 which lie at an axial distance along the distributor pipe, which corresponds to the sequence of four flow channels 10 arranged one behind the other.
  • Openings 7 are provided on each distributor pipe of the two-chamber distributor arrangement 3 and connect the upper chamber 4, which is connected to the coolant circulation system U II , to the flow channels 10 4 , 10 8 , 10 12 etc.
  • the coolant of the circulation system U II introduced into the chamber 4 therefore only reaches these selected flow channels, as is shown in FIGS. 4A and 4B by non-hatched areas.
  • the sequence of the openings 8 of the lower chamber 5 of the two-chamber distributor arrangement 3 connected to the dampening solution circulation system U I is such that only the flow channels 10 1 , 10 3 , 10 5 etc. are acted upon with the dampening solution which is in the circulation system U I circulates as hatched in Figures 4A and 4B.
  • one flow channel, for example 10 2 for the refrigerant between a pair of flow channels, for example 10 1 , 10 3 for the dampening solution and one flow channel, for example 10 4 , for the coolant between a pair of flow channels, for example 10 3 , 10 5 , for the dampening solution comes to rest.
  • Cold energy can thus be transferred directly from the refrigerant to the dampening solution, but not directly to the coolant. Rather, the coolant will only be able to obtain cooling energy indirectly via the dampening solution.
  • the first heat exchange function therefore enables primary transfer of cooling energy to the dampening solution circulation system U I. Excessive cooling energy can be stored in the buffer store 30 and, if necessary, can also be passed on to the coolant circulation system U II via the heat exchange device 1.
  • the second heat exchange function is shown in FIGS. 5A and 5B and is characterized in that, analogously to the above-described mode of operation, the openings 9 of the single-chamber distributor arrangement 6 are spaced such that the sequence of flow channels 10 2 , 10 4 , 10 6 etc. is charged with the refrigerant.
  • the openings 7, 8 of the two-chamber distributor arrangement 3 are provided such that the flow channels 10 3 , 10 6 , 10 9 etc. with the dampening solution and the flow channels 10 1 , 10 5 , 10 9 , 10 13 etc. with the coolant be supplied.
  • the refrigerant has a direct heat-exchanging relationship with the other two fluids, without these having a direct heat-exchanging relationship with one another.
  • the third heat exchange function is shown in FIGS. 6A and 6B and is characterized in that the refrigerant acts on the flow channels 10 3 , 10 6 , 10 9 etc., while the openings 7, 8 of the two-chamber distributor arrangement 3 are arranged in such a way that the dampening agent acts on the flow passages 10 2 , 10 5 , 10 8 , 10 11 etc. and the coolant acts on the flow passages 10 1 , 10 4 , 10 7 , 10 10 etc.
  • the third heat exchange function therefore has an immediate heat exchange relationship among all fluids. This enables the integration of a buffer memory similar to the buffer memory 30 in both circulation systems U I and U II .
  • the heat exchange preferably takes place between neighboring ones Flow channels 10 take place in countercurrent by this in opposite directions from the respective fluid be flowed through.
  • Each opening 7, 8, 9 of the manifolds of the two-chamber manifold assembly 3 or single chamber manifold assembly 6 can with the relevant flow channel 10 corresponding to the desired heat exchange function soldered or in another Be hermetically sealed.
  • A can Plate exchanger with basically unchanged basic structure be used.
  • the distribution pipes 3, 6 could also can be arranged interchangeably Heat exchange device according to the invention by mere Exchange of the two-chamber distributor arrangement 3 and / or Single chamber manifold assembly 6 for another To be able to convert heat exchange function.
  • Finally, could instead of a two-chamber distributor arrangement, also separate ones Single chamber manifold arrangements for each fluid be provided.
  • the pump 34 When the refrigeration device is switched on and the three-media heat exchange device 1 is acted upon with refrigerant, the pump 34 is started, while the pump 41 of the coolant circulation system U II is out of operation.
  • the buffer store 30 is thus continuously supplied with cooled dampening solution.
  • a partial amount of the dampening solution circulated in the circulation system U II by the pump 34 circulates via the branch line 33 into the storage container 32 for further processing by the dampening solution application device.
  • the pump 35 is dimensioned such that a sufficient volume flow of dampening solution always passes through the three-medium heat exchange device 1.
  • the dampening solution is cooled in the three-medium heat exchange device 1 as a function of the dampening solution temperature determined by the temperature sensor 35 on the downstream side of the buffer store 30.
  • the pumps 34 and 41 are in operation, so that all three fluids pass through the three-medium heat exchange device 1 when the refrigeration device is switched on.
  • the coolant flowing through the three-media heat exchange device 1 draws cold energy from the direct heat exchange with the coolant-cooled dampening solution, the buffer accumulator 30 ensuring that a sufficient amount of dampening solution is always available for cooling the coolant. This can also be supported by the fact that the temperature of the dampening solution in the circulation system U I is preferably set to a sufficiently low value.
  • the setting one for the roller application device suitable temperature of the coolant is carried out using the depending on the temperature sensor on the downstream side 42 measured temperature controlled control valve 40. At too low coolant temperature, the heater 45 in the bypass line 43 are put into operation by the the bypass line 43 constantly flowing coolant portion to warm up.
  • This operating mode corresponds essentially to that with the exception that the The refrigeration system is only put into operation when required is by the necessary for cooling the coolant Cooling energy primarily that in the buffer storage 30 stored amount of dampening solution is withdrawn.
  • a Loss of energy due to the circulation of dampening solution through the Secondary circuit is because of the dampening solution application device is out of order, negligible. If necessary, a could also be in the branch line 33 Shut-off valve can be arranged to flow the Completely switch off dampening solution by the secondary circuit.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Temperature (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP98109590A 1997-09-15 1998-05-27 Arrangement pour tempérer dans une machine d'impression Expired - Lifetime EP0911156B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE29716582U DE29716582U1 (de) 1997-09-15 1997-09-15 Temperierungsanordnung bei Druckmaschinen
DE29716582U 1997-09-15

Publications (2)

Publication Number Publication Date
EP0911156A1 true EP0911156A1 (fr) 1999-04-28
EP0911156B1 EP0911156B1 (fr) 2001-08-01

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EP98109590A Expired - Lifetime EP0911156B1 (fr) 1997-09-15 1998-05-27 Arrangement pour tempérer dans une machine d'impression

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US (1) US5974817A (fr)
EP (1) EP0911156B1 (fr)
DE (2) DE29716582U1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1710079A1 (fr) * 2005-04-07 2006-10-11 Technotrans AG Machine d'impression avec dispositif de contrôle de la température
WO2011019909A1 (fr) * 2009-08-14 2011-02-17 Johnson Controls Technology Company Système de réfrigération à refroidissement naturel
US11175076B2 (en) 2009-03-24 2021-11-16 Johnson Controls Technology Company Free cooling refrigeration system

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Publication number Priority date Publication date Assignee Title
FR2775066B1 (fr) * 1998-02-18 2000-06-02 Joel Bucaille Plaque destinee a former un echangeur et procede d'utilisation
DE19857107A1 (de) * 1998-12-10 2000-06-15 Baldwin Grafotec Gmbh Temperiervorrichtung für Druckmaschinen
US6508069B2 (en) 2000-02-29 2003-01-21 Peter M. Sibilia Temperature controlled gravity feed fountain solution supply apparatus
DE10190901D2 (de) * 2000-03-16 2005-09-15 Becker Kg Gebr Verfahren und Vorrichtung zur Nutzung bei einer Saug- /Druckluftversorgung an einer Druckmaschine anfallenden Abwärme
DE10013439C1 (de) * 2000-03-17 2001-08-23 Xcellsis Gmbh Wärmeübertrager in Schichtbauweise und Verwendung desselben
US6327865B1 (en) * 2000-08-25 2001-12-11 Praxair Technology, Inc. Refrigeration system with coupling fluid stabilizing circuit
DE10111614B4 (de) * 2001-03-10 2004-02-12 Technotrans Ag Feuchtmittel-Zufuhrsystem
SE525022C2 (sv) * 2003-04-17 2004-11-09 Ep Technology Ab Förångare och värmeväxlare med extern slinga
DE10354454B4 (de) 2003-11-21 2009-11-26 Technotrans Ag Temperiervorrichtung für Druckmaschinen
DE102005005303A1 (de) * 2005-01-05 2006-07-13 Koenig & Bauer Ag Systeme zur Temperierung von Bauteilen einer Druckmaschine
DE102005042302A1 (de) * 2005-09-06 2007-03-08 Baldwin Germany Gmbh Druckmaschinen-Reinigungsflüssigkeitsversorgungseinrichtung
DE102005042303A1 (de) * 2005-09-06 2007-03-08 Baldwin Germany Gmbh Druckmaschinen-Reinigungsflüssigkeits-Versorgungseinrichtung
JP4324187B2 (ja) * 2006-10-25 2009-09-02 トヨタ自動車株式会社 蓄熱装置
ITPD20070279A1 (it) * 2007-08-20 2009-02-21 Mta Spa Scambiatore di calore multifluido
EP2182309A1 (fr) * 2008-10-28 2010-05-05 Siemens Aktiengesellschaft Agencement pour le refroidissement d'une machine électrique
EP3270068B1 (fr) * 2009-07-28 2025-04-16 Carrier Japan Corporation Unite source de chaleur
IT1402297B1 (it) * 2010-09-08 2013-08-28 Uteco Converting Spa Struttura di cilindro retinato particolarmente per macchine da stampa flessografiche
JP5910517B2 (ja) * 2012-02-02 2016-04-27 株式会社デンソー 熱交換器
DE102012103850B3 (de) * 2012-05-02 2013-07-25 Windmöller & Hölscher Kg Vorrichtung zur Einstellung eines Betriebsparameters einer Farbe für einen Druckprozess einer Rotationsdruckmaschine sowie Verfahren hierzu
US10914540B1 (en) * 2019-08-29 2021-02-09 Yung-Cheng Chuang Water cooling system for providing water with constant temperature

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EP0713767A1 (fr) * 1994-11-25 1996-05-29 Technotrans Gmbh Arrangement pour tempérer un liquide de mouillage et/ou des rouleaux sélectionnés d'une machine d'impression
DE19628561C1 (de) * 1996-07-16 1997-09-04 Laengerer & Reich Gmbh & Co Plattenwärmetauscher

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Patent Citations (2)

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Publication number Priority date Publication date Assignee Title
EP0713767A1 (fr) * 1994-11-25 1996-05-29 Technotrans Gmbh Arrangement pour tempérer un liquide de mouillage et/ou des rouleaux sélectionnés d'une machine d'impression
DE19628561C1 (de) * 1996-07-16 1997-09-04 Laengerer & Reich Gmbh & Co Plattenwärmetauscher

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1710079A1 (fr) * 2005-04-07 2006-10-11 Technotrans AG Machine d'impression avec dispositif de contrôle de la température
EP2018964A1 (fr) * 2005-04-07 2009-01-28 technotrans AG Machine d'impression avec dispositif de contrôle de la température
US11175076B2 (en) 2009-03-24 2021-11-16 Johnson Controls Technology Company Free cooling refrigeration system
WO2011019909A1 (fr) * 2009-08-14 2011-02-17 Johnson Controls Technology Company Système de réfrigération à refroidissement naturel
US11199356B2 (en) 2009-08-14 2021-12-14 Johnson Controls Technology Company Free cooling refrigeration system

Also Published As

Publication number Publication date
US5974817A (en) 1999-11-02
DE59801115D1 (de) 2001-09-06
DE29716582U1 (de) 1997-11-06
EP0911156B1 (fr) 2001-08-01

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