EP0665940B1 - Systeme combine de chauffage et de refrigeration - Google Patents

Systeme combine de chauffage et de refrigeration Download PDF

Info

Publication number
EP0665940B1
EP0665940B1 EP94926210A EP94926210A EP0665940B1 EP 0665940 B1 EP0665940 B1 EP 0665940B1 EP 94926210 A EP94926210 A EP 94926210A EP 94926210 A EP94926210 A EP 94926210A EP 0665940 B1 EP0665940 B1 EP 0665940B1
Authority
EP
European Patent Office
Prior art keywords
piston
heat transfer
heat
cold
transfer means
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.)
Expired - Lifetime
Application number
EP94926210A
Other languages
German (de)
English (en)
Other versions
EP0665940A1 (fr
Inventor
Peter Hofbauer
Klaus Heikrodt
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.)
Robert Bosch GmbH
Viessmann Werke GmbH and Co KG
Original Assignee
Robert Bosch GmbH
Viessmann Werke GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH, Viessmann Werke GmbH and Co KG filed Critical Robert Bosch GmbH
Publication of EP0665940A1 publication Critical patent/EP0665940A1/fr
Application granted granted Critical
Publication of EP0665940B1 publication Critical patent/EP0665940B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
    • F02G1/0445—Engine plants with combined cycles, e.g. Vuilleumier
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2250/00—Special cycles or special engines
    • F02G2250/18—Vuilleumier cycles

Definitions

  • the invention relates to a regenerative Gas cycle heat and chiller working with two In a pressure-tight housing, the piston moves linearly together limit a warm work volume and of which the one piston in the housing is a hot one, with warmth applied working volume and the other piston cold working volume limited, the three Working volumes with the interposition of regenerators and heat exchangers are interconnected and a Drive and / or a control for the pistons provided is.
  • the invention is based on the task, a heat and Chiller of the type defined in the beginning to train that a high Heat transfer efficiency results in a compact design.
  • the solution to this problem by the invention is characterized in that the warm and cold Working volume through its piston crown from each other separating piston is cup-shaped and that be Piston jacket as a separation between the outside warm Heat exchanger and the internal cold Heat exchanger is used, the heat transfer from the or to the working medium in both heat exchangers between the outer and the inner surface of the Piston jacket and the associated surface of each Heat exchanger takes place.
  • the inventive arrangement of the cold heat exchanger results in a cup-shaped cold piston a short and small diameter construction of the Machine. A further reduction in the construction volume will achieved in that the piston skirt at the same time as a separation between the hot and cold heat exchanger.
  • the Construction according to the invention also creates a high efficiency for heat transfer because additional Partitions are eliminated, the heat and flow losses Episode.
  • the cold one Piston according to another feature of the invention at least partially made of poorly heat-conducting material.
  • the cold piston is preferably at least on one Provide side with poor heat-conducting material.
  • the surface affected by the working medium the heat exchanger by applying porous material, by corrugations or grooves and / or by use corrugated or grooved sheets can be enlarged.
  • the heat exchangers in two parts each with an open Provided channels, as a liner for the cold piston trained body and from an open side of the Channels sealing body formed. Because of the pressure in the channels of the heat exchanger considerably less than is the pressure of the working medium, presses the working medium the body in both heat exchangers against the Sealing body, so that special and expensive sealing measures in the heat exchangers designed according to the invention can be dispensed with. As the overpressure of the Working medium over the base body also the sealing body of the presses the warm heat exchanger against the machine housing, can the connections for the warm heat exchanger flowing medium can be carried out easily.
  • the sealing body the heat exchanger made of heat-insulating material manufactured, which is a significant reduction in unwanted heat conduction from the respective heat exchanger in the housing results.
  • the invention proposes between the warm heat exchanger and this on the process side downstream regenerator interacting with the piston skirt To arrange sealing ring. This will turn on easily achieved that the working medium after Leaving the warm heat exchanger via the downstream one Regenerator is led to the cold heat exchanger.
  • Heating and cooling machine in a longitudinal section shown.
  • the machine shown in longitudinal section includes a as Circular cylinder formed pressure-tight housing 1, the is provided at one end with a flange la to which a motor housing 2 screwed with a corresponding flange 2a becomes.
  • the motor housing 2 is only partially shown.
  • the pressure-tight housing 1 with one Provided housing cover 4, which in the exemplary embodiment Thread is screwed to the cylindrical housing 1 and in which a heat generator in the form of a gas burner 5 is arranged.
  • This gas burner comprises a cylindrical one Supply pipe 5a for the fuel gas, the outlet side with a metering hemisphere 5b is provided.
  • Concentric too this dosing hemisphere 5b is a reaction surface acting burner surface 5c made of a stainless steel mesh arranged, which limits the gas inflow chamber and at Operation of the gas burner glows, so that the gas burner 5 one Most of the heat generated is emitted by radiation.
  • the resulting flue gases become hemispherical Burner surface 5c surrounding combustion chamber 5d through an exhaust pipe 5e deducted, the supply pipe 5a of the gas burner 5 concentric surrounds.
  • the heat generated by the gas burner 5 is generated by radiation and Convection delivered to a partition 6, which is rotationally symmetrical Conic section, in the embodiment is designed as a hemisphere and in the interior of the housing 1 bulges.
  • the hemispherical runs Curvature with constant distance to semi-conical burner surface 5c of the gas burner 5.
  • the partition designed as part of the pressure-tight housing 1 6 is attached to a support ring 6a, which has a membrane-like extension 6b with the end of the cylindrical Housing 1 is connected. In the embodiment both connections by welding.
  • Isolation rings 7a and 7b each on one side of the membrane-like extension 6b on the one hand to the housing cover 4 and on the other hand to the housing 1, the Heat dissipation from that heated by the gas burner 5 Partition 6 to the housing 1 and its housing cover 4 and thus significantly reduced to the environment.
  • the heat generated by the gas burner 5 and absorbed by the partition is given off from the inside of the partition 6 to a working medium, preferably helium, which is in a hot working volume V h .
  • This hot working volume V h is limited on the one hand by the partition 6 and on the other hand by the piston crown 8a of a piston 8 which is arranged in the housing 1 so as to be linearly movable.
  • This piston 8 is connected via a piston rod 8b to a motor or controller arranged in the motor housing 2, which are not shown in the drawing.
  • These three volumes are interconnected with the interposition of regenerators R h , R k and heat exchangers W w , W k .
  • the regenerator R h arranged in the hot part of the housing 1 stores part of the heat given off to the hot working volume V h during the course of the regenerative gas cycle process; the regenerator R k arranged in the cold part of the housing 1 performs the corresponding function with regard to the cold working volume V k .
  • the heat exchanger W k which in the exemplary embodiment is arranged within the cold piston 9 in a stationary manner on the base 3, is continuously supplied with a medium taken from the environment via a line 3 a arranged in the base 3, which medium is returned to the environment via a line 3 b after a portion of its heat content has been removed becomes.
  • the heat exchanger W w is fed through connecting lines 10a, 10b with a heat transfer medium, the heating of which, when the machine is used, serves as a heat machine for generating energy.
  • the shape of the piston crown 8a of the hot piston 8 is adapted to the shape of the curved partition 6.
  • a high flow velocity and thus a better heat transfer is achieved by this adapted shape, when the working medium from the shrinking hot working volume V h via the regenerator R h and the heat exchanger W w into the space for the warm working volume V w when the cycle is complete flows, which is formed between the two pistons 8 and 9.
  • a baffle 11 is arranged in the edge region of the partition 6. This baffle 11 forms flow channels with a small flow cross-section in the edge region of the partition wall 6, so that the working medium leaving the hot working volume V h is passed at high flow velocity over the edge region of the partition wall 6 before the working medium enters the regenerator R h .
  • the cold piston 9 separating the warm working volume V w from the cold working volume V k by its piston crown 9a is cup-shaped and provided with an insulating layer 9c on the inside of both its piston crown 9a and its piston skirt 9b.
  • the piston jacket 9b serves as a separation between the external heat exchanger W w and the internal cold heat exchanger W k .
  • heat is transferred in an annulus.
  • this is formed by the outer lateral surface of the piston jacket 9b and the inner surface of the heat exchanger W w .
  • the annular space results between the inner jacket surface of the piston jacket 9b provided with the insulating layer 9c and the surface of the cold heat exchanger W k .
  • both heat exchangers W w and W k are formed in two parts from a base body 12 and 13 and from a sealing body 14 and 15, respectively.
  • the base body 12 and 13 also serves as a liner for the cold piston 9.
  • each base body 12 and 13 is provided with channels 12a and 13a through which the respective heat transfer medium flows and which leads to the connecting lines 10a , 10b and 3a, 3b are connected.
  • the channels 12a and 13a which are open on one side, are covered by the respective sealing body 14 and 15, respectively.
  • the connecting lines 10a and 10b of the warm heat exchanger W w leading into the pressure-tight housing 1 can also be designed without problems.
  • the surface of the base body 12 or base body 13 serving as the running surface for the piston 9 is designed with grooves 12b or 13b through which the working medium flows and which at the same time the surface of the heat exchanger W participating in the heat transfer Increase w or W k .
  • the base bodies 12 and 13 can also be corrugated or be formed with a porous surface.
  • the sealing body 14 and 15 are preferably made of heat-insulating material in order to avoid unwanted heat dissipation from the respective heat exchanger W w or W k .
  • a sealing ring 16 which interacts with the piston skirt 9a is arranged between the warm heat exchanger W w and the regenerator R k connected downstream on the process side thereof. This sealing ring 16 ensures that the working medium in its flow between the heat exchangers W w and W k is passed through the cold regenerator R k , which is arranged in an extension of the base body 12 on the inside of the housing 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention concerne un système combiné de chauffage et de réfrigération fonctionnant selon un procédé à régénération du cycle gazeux, qui comprend deux pistons (8, 9) se déplaçant linéairement dans un boîtier (1) étanche à la pression, qui délimitent conjointement un volume de travail chaud (Vw). Un (8) des pistons délimite dans le boîtier (1) un volume de travail chaud (Vh) soumis à l'application de chaleur, l'autre piston (9) délimite quant à lui un volume de travail (Vk) froid. Les trois volumes de travail (Vh, Vw, Vk) sont reliés entre eux par l'intermédiaire de régénérateurs (Rh, Rk) et d'échangeurs de chaleur (Ww, Wk). Afin d'obtenir un rendement élevé du transfert de chaleur, dans une structure compacte, le piston (9) qui sépare par sa base (9a) le volume de travail chaud du volume de travail froid (Vw, Vk, se présente sous forme de pot. Le corps du piston (9b) sert à séparer l'échangeur de chaleur chaud (Ww) situé à l'extérieur de l'échangeur de chaleur (Wk) froid, situé à l'intérieur. Pour les deux échangeurs de chaleur (Ww, Wk), le transfert de chaleur s'effectue entre la surface extérieure ou la surface intérieure du corps du piston (9b) et la surface correspondante de l'échangeur de chaleur (Ww ou Wk) concerné.

Claims (7)

  1. Système combiné de chauffage et de réfrigération utilisant le procédé de circulation de gaz avec régénération, comprenant deux pistons (8, 9) mobiles en translation dans un boítier (1) étanche à la pression, ces pistons délimitant un volume actif (Vw), chaud, commun, et l'un des pistons (8) délimite dans le boítier (1) un volume actif (Vh), chaud, recevant de la chaleur et l'autre piston (9) délimite un volume actif (Vk), froid, les trois volumes actifs (Vh, Vw, Vk) étant reliés avec interposition de régénérateurs (Rh, Rk) et d'échangeurs de chaleur (Ww, Wk), les pistons (8, 9) état munis d'un moyen d'entraínement et/ou de commande,
    caractérisé en ce que
    le piston (9), dont le fond (9a) sépare l'un de l'autre le volume actif chaud et le volume actif froid (Vw, Vk), a une forme de pot et la jupe (9b) du piston sert de séparation entre l'échangeur de chaleur chaud (Ww) situé à l'extérieur et l'échangeur de chaleur froid (Wk) situé à l'intérieur, l'échange de chaleur avec le fluide caloporteur dans les deux échangeurs de chaleur (Ww, Wk) se faisant entre la surface enveloppe extérieure ou la surface enveloppe intérieure de la jupe (9b) du piston, et la surface extérieure correspondante de l'échangeur de chaleur respectif (Ww ou Wk).
  2. Système combiné de chauffage et de réfrigération selon la revendication 1,
    caractérisé en ce que
    le piston (9) délimitant le volume actif froid est au moins partiellement réalisé en une matière mauvaise conductrice de la chaleur.
  3. Système combiné de chauffage et de réfrigération selon la revendication 2,
    caractérisé en ce que
    le piston (9) délimitant le volume actif froid est muni au moins d'un côté d'une matière mauvaise conductrice de chaleur (couche isolante 9c).
  4. Système combiné de chauffage et de réfrigération selon au moins l'une des revendications 1 à 9,
    caractérisé en ce que
    la surface de l'échangeur de chaleur (Ww, Wk) recevant le fluide caloporteur est augmentée par l'application d'une matière poreuse, par des ondulations ou des rainures (12b, 13b) et/ou par l'utilisation de tôles ondulées ou rainurées.
  5. Système combiné de chauffage et de réfrigération selon au moins l'une des revendications 1 à 4,
    caractérisé en ce que
    les échangeurs de chaleur (Ww, Wk) sont formés d'un corps de base (12, 13), en forme de chemise, muni de canaux ouverts (12a, 13a) pour le piston (9) et d'un corps d'étanchéité (14, 15) fermant les côtés ouverts des canaux (12a, 13a).
  6. Système combiné de chauffage et de réfrigération selon la revendication 5,
    caractérisé en ce que
    le corps d'étanchéité (14, 15) est réalisé en une matière isolante thermique.
  7. Système combiné de chauffage et de réfrigération selon au moins l'une des revendications 1 à 6,
    caractérisé en ce qu'
    un joint d'étanchéité (16), coopérant avec l'enveloppe (9b) du piston, est prévu entre l'échangeur de chaleur chaud (Ww) et le régénérateur (Rk) en aval de celui-ci, du côté du procédé.
EP94926210A 1993-08-28 1994-08-19 Systeme combine de chauffage et de refrigeration Expired - Lifetime EP0665940B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4328993 1993-08-28
DE4328993A DE4328993C2 (de) 1993-08-28 1993-08-28 Maschine zum Heizen und/oder Kühlen
PCT/EP1994/002753 WO1995006847A1 (fr) 1993-08-28 1994-08-19 Systeme combine de chauffage et de refrigeration

Publications (2)

Publication Number Publication Date
EP0665940A1 EP0665940A1 (fr) 1995-08-09
EP0665940B1 true EP0665940B1 (fr) 1998-03-04

Family

ID=6496259

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94926210A Expired - Lifetime EP0665940B1 (fr) 1993-08-28 1994-08-19 Systeme combine de chauffage et de refrigeration

Country Status (7)

Country Link
EP (1) EP0665940B1 (fr)
JP (1) JPH08503062A (fr)
KR (1) KR950704661A (fr)
BR (1) BR9405561A (fr)
DE (1) DE4328993C2 (fr)
ES (1) ES2114219T3 (fr)
WO (1) WO1995006847A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4401247C2 (de) * 1994-01-18 1998-10-08 Bosch Gmbh Robert Wärmeübertrager
DE19516499A1 (de) * 1995-05-05 1996-12-05 Bosch Gmbh Robert Verfahren zur Abgaswärmenutzung bei Wärme- und Kältemaschinen

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1240862A (en) * 1915-09-21 1917-09-25 Ivar Lundgaard Refrigerating-machine.
US1275507A (en) * 1917-01-29 1918-08-13 Rudolph Vuilleumier Method and apparatus for inducing heat changes.
JPH0660770B2 (ja) * 1986-03-25 1994-08-10 川崎重工業株式会社 熱駆動ヒ−トポンプ
JP2500447Y2 (ja) * 1991-03-28 1996-06-05 サムスン エレクトロニクス カンパニー リミテッド ボルマイア―ヒ―トポンプ
DE4206957A1 (de) * 1992-03-05 1993-09-16 Viessmann Werke Kg Aussenbeheizte, regenerative, nach dem vuilleumier-kreisprozess arbeitende waerme- und kaeltemaschine

Also Published As

Publication number Publication date
KR950704661A (ko) 1995-11-20
DE4328993A1 (de) 1995-03-09
BR9405561A (pt) 1999-09-08
EP0665940A1 (fr) 1995-08-09
ES2114219T3 (es) 1998-05-16
DE4328993C2 (de) 1995-11-30
JPH08503062A (ja) 1996-04-02
WO1995006847A1 (fr) 1995-03-09

Similar Documents

Publication Publication Date Title
DE4401247C2 (de) Wärmeübertrager
EP0665941B1 (fr) Systeme combine de chauffage et de refrigeration
CH635166A5 (de) Hubkolbenmaschine, insbesondere heissgasmaschine oder verdichter.
DE19612616C2 (de) Stirlingmotor
EP0749525A1 (fr) Dispositif permettant de faire fonctionner et de commander un moteur stirling a piston libre
DE112011103773T5 (de) Kombinierte Kammerwand und Wärmetauscher
EP0769122B1 (fr) Exploiter la chaleur des gaz brûlés dans des machines thermiques et frigorifiques à régénérateur
EP0665940B1 (fr) Systeme combine de chauffage et de refrigeration
DE10319806B4 (de) Wärmekraftmaschine nach dem idealen Stirlingprinzip
DE19601579C2 (de) Wärmeübertrager
DE4216132C2 (de) Kompressionswärmepumpe
DE4401246A1 (de) Regenerator
DE2326203C3 (de) Heißgaskolbenmaschine
DE4232555A1 (de) Heißgasmotor mit äußerer Verbrennung und geschlossenem Kreisprozeß
WO2010015225A1 (fr) Moteur stirling
DE10229442B4 (de) Wärmetauscher zur Abkühlung des Arbeitsgases eines Stirlingmotors
DE3536710A1 (de) Waermewandler und verfahren zu seinem betrieb
EP1049864B1 (fr) Regenerateur et procede de production d'un regenerateur
DE3403481A1 (de) Thermischer kompressor
EP1180656A1 (fr) Echangeur de chaleur en spirale
DE3327483A1 (de) Regenerative waermekraftmaschine
DE1751184C3 (de) Heissgaskolbenmaschine
DE3242658A1 (de) Thermo-mechanischer energiewandler
DE3003261A1 (de) Verfahren und maschine zur nutzbarmachung von waermekraft
DE202004020453U1 (de) Wärmekraftmaschine nach dem Stirling-Prinzip

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19950422

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH ES FR GB IT LI SE

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 19961028

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH ES FR GB IT LI SE

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: VIESSMANN WERKE GMBH & CO

Owner name: ROBERT BOSCH GMBH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

ET Fr: translation filed
ITF It: translation for a ep patent filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2114219

Country of ref document: ES

Kind code of ref document: T3

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19980507

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19980924

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 19981019

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19981021

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19981027

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19981113

Year of fee payment: 5

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990819

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990820

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19990830

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990831

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19990831

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19990819

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000428

EUG Se: european patent has lapsed

Ref document number: 94926210.9

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20000911

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050819