EP0723123A1 - Système de combustion insonorisée et amortisseur pour un tel système - Google Patents

Système de combustion insonorisée et amortisseur pour un tel système Download PDF

Info

Publication number
EP0723123A1
EP0723123A1 EP96200151A EP96200151A EP0723123A1 EP 0723123 A1 EP0723123 A1 EP 0723123A1 EP 96200151 A EP96200151 A EP 96200151A EP 96200151 A EP96200151 A EP 96200151A EP 0723123 A1 EP0723123 A1 EP 0723123A1
Authority
EP
European Patent Office
Prior art keywords
combustion system
container
wall
flexible
rigid
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
EP96200151A
Other languages
German (de)
English (en)
Other versions
EP0723123B1 (fr
Inventor
Gerard Westendorp
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.)
Nefit Buderus BV
Original Assignee
Nefit Fasto BV
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 Nefit Fasto BV filed Critical Nefit Fasto BV
Publication of EP0723123A1 publication Critical patent/EP0723123A1/fr
Application granted granted Critical
Publication of EP0723123B1 publication Critical patent/EP0723123B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/16—Silencing apparatus characterised by method of silencing by using movable parts
    • F01N1/22—Silencing apparatus characterised by method of silencing by using movable parts the parts being resilient walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M20/00—Details of combustion chambers, not otherwise provided for, e.g. means for storing heat from flames
    • F23M20/005—Noise absorbing means

Definitions

  • the invention relates to a sound-damped combustion system.
  • the invention also relates to an acoustic damper to be used in such a combustion system.
  • combustion systems such as boilers for heating, produce noise which is caused, inter alia, by the combustion process.
  • the flame occurring during the combustion in acoustic respects is a source of noise and an amplifier for frequencies between zero and one thousand Hertz.
  • Other noise sources in combustion systems are, for example, fans, gas flows in the system, etc.
  • Helmholtz resonators offer little or no relief for acoustic problems which are broad band and occur particularly in the low-frequency range (0-250 Hz).
  • Helmholtz resonators would have to have relatively large, unwieldy dimensions for damping at very low frequencies.
  • the object of the invention is to provide a combustion system based on a totally different damping principle, in which noise can be damped over a broad frequency range.
  • Another object of the invention is to offer a compact solution to the abovementioned noise problems.
  • the invention provides a combustion system which is characterized in that a predetermined part of an otherwise rigid wall of the system, an otherwise rigid wall of an air inlet duct of the system and/or an otherwise rigid wall of a flue gas duct of the system is flexible.
  • the flexible wall part acts as a mechanical resonator, and has a very low impedance for the envisaged frequency range.
  • an acoustic "short-circuit" occurs at this place. Viewed from the flame, the acoustic impedance changes through this measure. Moreover, the acoustic losses can increase.
  • a strong resonator also introduces new resonances around the natural frequency of the resonator. It is found that this undesirable side-effect can be suppressed effectively by covering the outside of the flexible wall part with a container made of a rigid material whose edges connect to the rigid part of the wall, the volume bounded by the flexible wall part and the container being in communication with the environment of the container by way of at least one opening in the container wall.
  • This environment can be the ambient air around the combustion system, but it can also relate to other parts of the damping system according to the invention, as will emerge from what follows below.
  • the quantity of air in the container acts like an air spring which is much more rigid than the flexible wall part. This means that the movement of the air through the flexible wall part is passed on by the air spring to the opening in the container, where friction is consequently created.
  • the desired damping effect can be set by adapting the measurements of the opening.
  • the natural frequency of the flexible wall part is determined by the degree of flexibility and the mass thereof. If a very low natural frequency is desired, for example 20 Hz, the flexible wall part would have to be relatively soft, and its mass would have to be very great.
  • a pipe of a predetermined length and cross-section which is open at both ends is fitted in communication with each opening of the volume bounded by the flexible wall part and the container.
  • the weight of the air in the pipe transformed by the ratio of the square of the surface area of the flexible wall part to the square of the surface area of the pipe cross-section, has the effect of a considerable weight on the flexible wall part.
  • the damping characteristics of such a construction can be set further by selecting a suitable length and cross-section for each pipe.
  • flexible wall parts are placed in series, for example by making a predetermined part of the otherwise rigid container wall locally flexible.
  • Both the rigid and the flexible container wall part can contain the abovementioned opening(s) with the damping action.
  • the outside of the flexible container wall part of a container can be covered by a next container made of a rigid material whose edges connect to the rigid part of the wall of the first-mentioned container.
  • the abovementioned pipe communicating with an opening in the container wall can form a connection between two or more different containers.
  • An opening in the flexible container wall part can also form a connection between two adjacent containers.
  • Each additional container has to damp higher frequencies than a preceding container.
  • This effect can advantageously be achieved through the fact that the flexibility of the flexible wall parts decreases per flexible wall part in the direction of the outside of the combustion system and/or by making the dimensions of the flexible wall parts decrease per flexible wall part in the direction of the outside of the combustion system.
  • the flexible wall part forms part of the wall of a Helmholtz resonator.
  • a conventional Helmholtz resonator for a specific frequency can thus advantageously be combined with the damping measures according to the invention for a broad frequency range.
  • the mass of the flexible wall part for the damping of in particular low frequencies is increased by placing on the flexible wall part with a specific surface area a layer of material with a smaller surface area than said surface area.
  • the flexible wall part is not active if there is a pressure minimum in the gas at the position of the flexible wall part. However, it is possible more or less to fix such a pressure minimum at some distance from a flexible wall part by providing a narrowing of the passage locally over some length in the system, the air inlet duct or the flue gas duct.
  • the flexible wall part is preferably formed by a membrane of a fluorine-containing polymer, such as PVDF, or stainless steel, materials which can readily withstand high temperatures and show few ageing phenomena.
  • a fluorine-containing polymer such as PVDF, or stainless steel
  • the measures according to the invention are preferably used in a boiler for central heating and/or heating of running water, in particular in the flue gas duct thereof.
  • Figs. 1, 2, 2a and 3 show a damper 2 which comprises a housing part 4, a membrane 6 and a container 8.
  • the damper is intended to form part of a flue gas duct of a combustion system, for example a boiler for central heating and/or the heating of running water.
  • the flow of flue gases through the damper 2 is illustrated in Fig. 2 by arrows 10.
  • the membrane 6 is clamped along its edges between flanges of the housing part 4 and the container 8.
  • the membrane 6 can be glued between the flanges, but it is also possible to clamp the membrane between the flanges by means of a screw connection or the like between the flanges.
  • the housing part 4 and the container 8 are made of a rigid material such as a plastic or a metal, while the membrane 6 is so flexible that it can be impinged upon by the noise pressure in the combustion system and in that case starts acting like a mass-spring damper system.
  • a resonance in the flue gas duct is greatly reduced in a predetermined frequency range.
  • the container 8 is provided with an opening 12 which leads to an open pipe 14 which at its free end is in open communication with the environment, i.e. the ambient air of the damper.
  • the membrane 6 and the container 8 bound an air spring, which has been made leaky by means of the opening 12 leading to the environment. Since the air spring is much more rigid than the membrane 6, the air spring acts as a conductor of the air movement through the membrane 6 to the opening 12 and the pipe 14, where the air encounters friction. This produces a vibration damping which can be set to a desired frequency range by making a suitable selection of the dimensions of the opening 12 and those of the pipe 14, in particular the length thereof.
  • the container 8 can comprise several openings, each with or without a pipe.
  • the damper can be provided at some distance from the membrane 6 with an element 13 with the function of narrowing the passage locally over some length, so that a pressure minimum in the gas flowing through the damper is not "fixed" at the membrane 6, but at the position of the element 13.
  • Fig. 4 shows on a slightly enlarged scale a damper 2a comprising a housing part 4 and a membrane 6.
  • the damper 2a is connected to an only roughly shown combustion system 16.
  • the damper 2a according to Fig. 4 comprises a number of containers 8a, 8b,..., 8x of a rigid material, and membranes 6a, 6b,..., 6x of a flexible material.
  • the volume formed by the membrane 6, the container 8a and the membrane 6a is provided with an opening 12a which communicates with a pipe 14a.
  • the volume formed by the membrane 6a, the container 8b and the membrane 6b is provided with an opening 12b which communicates with a pipe 14b which is shorter in length than the pipe 14a.
  • the volume formed by the membrane 6x and the container 8x is also provided with an opening 12x which communicates with an open pipe 14x which is shorter than all other pipes.
  • the membrane 6a is more rigid than the membrane 6
  • the membrane 6b is more rigid than the membrane 6a
  • the membrane 6x is more rigid than all other membranes.
  • two or more of the pipes 14a,...14x can be interconnected to form one (possibly branching) pipe, which interconnects the respective corresponding openings 12a,...12x.
  • One or more of the membranes 6a,...6x can also be provided with a damping connection opening.
  • Fig. 5 shows a damper 2b which, like the damper 2a of Fig. 4, comprises a number of series-connected containers 8aa and 8bb of a rigid material. Unlike the damper 2a of Fig. 4, the damper 2b of Fig. 5 has membranes 6 and 6aa of a flexible material, which membranes are all made of the same sheet-type material and differ from each other only as regards surface area.
  • the damper 2b can comprise more than the two containers 8aa and 8bb shown in Fig. 5 if required, as is suggested by dashed lines.
  • the container 8aa is provided with an opening 12aa which has an open pipe 14aa coupled thereto, and in a corresponding way the container 8bb is provided with an opening 12bb and an open pipe 14bb connecting thereto.
  • the container 8aa is active for damping relatively low frequencies, while higher frequencies are damped by means of the container 8bb.
  • a layer of material for example of bitumen, can be applied, for example glued, on one or more of the flexible wall parts 6, 6a-6x or 6aa according to Figs. 1 - 5, which layer of material has a smaller surface area than the membrane surface area, with the result that the membrane will no longer resonate at higher frequencies.
  • the layer of material on membrane 6 is indicated by reference number 16.
  • Fig. 6 shows a graph in which the frequency in Hz is plotted along the horizontal axis, while the sound pressure level in dB is plotted along the vertical axis.
  • Curve A shows the loudspeaker response of a certain heat exchanger of a combustion system without damping measure; curve B shows the loudspeaker response for the same heat exchanger after the fitting of a damper according to the invention.
  • the damping of the tops of the curve A over the frequency range shown is between 4 and 10 dB.
  • Fig. 7 illustrates a combination of a Helmholtz resonator 22 and a damper fitted near a combustion point 20 of a combustion system, comprising a membrane 24, a container 26 and an open pipe branch 28.
  • the Helmholtz resonator can, for example, damp a frequency of 300 Hz, while the membrane 24, the container 26 and the pipe branch 28 damp lower frequencies.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chimneys And Flues (AREA)
EP96200151A 1995-01-23 1996-01-22 Système de combustion insonorisée et amortisseur pour un tel système Expired - Lifetime EP0723123B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL9500116A NL9500116A (nl) 1995-01-23 1995-01-23 Geluidgedempt verbrandingssysteem, en demper bestemd voor gebruik in een dergelijk systeem.
NL9500116 1995-01-23

Publications (2)

Publication Number Publication Date
EP0723123A1 true EP0723123A1 (fr) 1996-07-24
EP0723123B1 EP0723123B1 (fr) 2000-04-05

Family

ID=19865480

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96200151A Expired - Lifetime EP0723123B1 (fr) 1995-01-23 1996-01-22 Système de combustion insonorisée et amortisseur pour un tel système

Country Status (3)

Country Link
EP (1) EP0723123B1 (fr)
DE (1) DE69607496T2 (fr)
NL (1) NL9500116A (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19612987A1 (de) * 1995-03-23 1996-09-26 Vaillant Joh Gmbh & Co Brennstoffbeheiztes Heizgerät
EP1213538A3 (fr) * 2000-12-08 2002-07-31 ABB Turbo Systems AG Dispositif pour gaz d'échappement comprenant un résonateur de Helmholtz
EP1233236A1 (fr) * 2001-02-15 2002-08-21 Immergas S.p.A. Dispositif pour la compensation des impulsions, en particulier pour les chaudières à gaz d'installations de chauffage
EP1624250A1 (fr) * 2004-08-03 2006-02-08 Siemens Aktiengesellschaft Dispositif pour atténuer les oscillations acoustiques dans les chambres combustion
EP1624251A1 (fr) * 2004-08-03 2006-02-08 Siemens Aktiengesellschaft dispositif pour atténuer les oscillations acoustiques dans les chambres combustion avec fréquence de résonance ajustable
WO2008116870A1 (fr) * 2007-03-28 2008-10-02 Mahle International Gmbh Résonateur de helmholtz
US8272475B2 (en) 2008-04-30 2012-09-25 Metso Paper, Inc. Sound attenuator for low frequencies, method for manufacturing sound attenuator for low frequencies and system for attenuating low frequencies for example in air-conditioning ducts of paper mills
FR2976619A1 (fr) * 2011-06-14 2012-12-21 Power Europ Systeme d'echappement de vehicule avec modulation sonore.

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004056898A1 (de) 2004-11-25 2006-06-01 Robert Bosch Gmbh Schalldämpfungseinrichtung für Heizgeräte
DE102005004079B4 (de) * 2005-01-28 2007-12-20 Robert Bosch Gmbh Schalldämpfungseinrichtung für ein Heizgerät

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL87151C (fr) * 1900-01-01
FR2504659A1 (fr) * 1981-04-28 1982-10-29 Sdecc Dispositif de securite pour chambre de combustion a paroi souple
DE3517859A1 (de) * 1985-05-17 1986-11-20 Wolf Klimatechnik GmbH, 8302 Mainburg Heizungskessel
DE4226890A1 (de) * 1992-07-17 1994-01-20 Grosschweiswerk Und Dampfkesse Einsatz für einen Abgaskamin

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL87151C (fr) * 1900-01-01
FR2504659A1 (fr) * 1981-04-28 1982-10-29 Sdecc Dispositif de securite pour chambre de combustion a paroi souple
DE3517859A1 (de) * 1985-05-17 1986-11-20 Wolf Klimatechnik GmbH, 8302 Mainburg Heizungskessel
DE4226890A1 (de) * 1992-07-17 1994-01-20 Grosschweiswerk Und Dampfkesse Einsatz für einen Abgaskamin

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19612987A1 (de) * 1995-03-23 1996-09-26 Vaillant Joh Gmbh & Co Brennstoffbeheiztes Heizgerät
EP1213538A3 (fr) * 2000-12-08 2002-07-31 ABB Turbo Systems AG Dispositif pour gaz d'échappement comprenant un résonateur de Helmholtz
US6705428B2 (en) 2000-12-08 2004-03-16 Abb Turbo Systems Ag Exhaust gas system with helmholtz resonator
EP1233236A1 (fr) * 2001-02-15 2002-08-21 Immergas S.p.A. Dispositif pour la compensation des impulsions, en particulier pour les chaudières à gaz d'installations de chauffage
EP1624250A1 (fr) * 2004-08-03 2006-02-08 Siemens Aktiengesellschaft Dispositif pour atténuer les oscillations acoustiques dans les chambres combustion
EP1624251A1 (fr) * 2004-08-03 2006-02-08 Siemens Aktiengesellschaft dispositif pour atténuer les oscillations acoustiques dans les chambres combustion avec fréquence de résonance ajustable
WO2008116870A1 (fr) * 2007-03-28 2008-10-02 Mahle International Gmbh Résonateur de helmholtz
US8272475B2 (en) 2008-04-30 2012-09-25 Metso Paper, Inc. Sound attenuator for low frequencies, method for manufacturing sound attenuator for low frequencies and system for attenuating low frequencies for example in air-conditioning ducts of paper mills
FR2976619A1 (fr) * 2011-06-14 2012-12-21 Power Europ Systeme d'echappement de vehicule avec modulation sonore.

Also Published As

Publication number Publication date
DE69607496T2 (de) 2000-11-23
DE69607496D1 (de) 2000-05-11
NL9500116A (nl) 1996-09-02
EP0723123B1 (fr) 2000-04-05

Similar Documents

Publication Publication Date Title
US7011180B2 (en) System for filtering ultrasonic noise within a fluid flow system
US7073534B2 (en) Silencer for perforated plate flow conditioner
EP0723123B1 (fr) Système de combustion insonorisée et amortisseur pour un tel système
US11073145B2 (en) Pressure pulsation traps
US20060096650A1 (en) Non-linear noise suppressor for perforated plate flow conditioner
DK0934457T3 (da) Gasströmningsdæmper
US20200224898A1 (en) Flow generation unit, air treatment plant comprising said flow generation unit and use of the latter for air treatment
Mekid et al. DESIGN OF HELMHOLTZ RESONATORS IN ONE AND TWO DEGREES OF FREEDOM FOR NOISE ATTENUATION IN PIPELINES.
JPS6010238B2 (ja) 配管系内気流体の脈動防止装置
AU672601B2 (en) Silencer for compressed air
US20220026059A1 (en) Pulsating combustion device with improved energy conversion efficiency and reduced noise level
RU200098U1 (ru) Глушитель шума выбросов пара
JP2002089228A (ja) 襞状騒音分離型消音器
JP2007107847A (ja) 絞り装置および冷媒用配管
JPH04219499A (ja) 遠心圧縮機の騒音減衰装置用の吸音材を予め圧縮する方法
GB2250356A (en) Noise attenuation in ducting
US20050061578A1 (en) Muffling device and method for internal combustion engine
RU2781900C1 (ru) Комбинированное устройство гашения колебаний давления в трубопроводах энергетических установок и снижения шума энергетических установок
EP0006955A1 (fr) Silencieux sans garniture.
EP4375573A1 (fr) Silencieux
Brandstätt et al. Noise reduction at heating system exhaust pipes
Kassim et al. Experimental Study of Pipes Shape Effect on Noise Reduction
JPH10266899A (ja) 圧力変動吸収装置および流体消費機器
Farooqui Noise reduction in centrifugal compressors using Helmholtz resonators
RU2279015C1 (ru) Вентиляционный шумоглушитель

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

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR GB IT NL

17P Request for examination filed

Effective date: 19960626

17Q First examination report despatched

Effective date: 19980506

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

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): DE ES FR GB IT NL

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

Ref country code: ES

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

Effective date: 20000405

REF Corresponds to:

Ref document number: 69607496

Country of ref document: DE

Date of ref document: 20000511

ET Fr: translation filed
ITF It: translation for a ep patent filed
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
NLT1 Nl: modifications of names registered in virtue of documents presented to the patent office pursuant to art. 16 a, paragraph 1

Owner name: NEFIT BUDERUS B.V.

REG Reference to a national code

Ref country code: FR

Ref legal event code: CD

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

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

Ref country code: IT

Payment date: 20100127

Year of fee payment: 15

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

Ref country code: GB

Payment date: 20110127

Year of fee payment: 16

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

Effective date: 20110122

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

Ref country code: FR

Payment date: 20120202

Year of fee payment: 17

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

Ref country code: DE

Payment date: 20130123

Year of fee payment: 18

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

Ref country code: NL

Payment date: 20130130

Year of fee payment: 18

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

Effective date: 20130122

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20130930

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: 20130122

Ref country code: FR

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

Effective date: 20130131

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 69607496

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: V1

Effective date: 20140801

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

Ref country code: DE

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

Effective date: 20140801

Ref country code: NL

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

Effective date: 20140801

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 69607496

Country of ref document: DE

Effective date: 20140801