DK156256B - Apparatus for vibration suppression of long-lasting buildings, such as chimneys, transmitters or similar elongated structures - Google Patents
Apparatus for vibration suppression of long-lasting buildings, such as chimneys, transmitters or similar elongated structures Download PDFInfo
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- DK156256B DK156256B DK613684A DK613684A DK156256B DK 156256 B DK156256 B DK 156256B DK 613684 A DK613684 A DK 613684A DK 613684 A DK613684 A DK 613684A DK 156256 B DK156256 B DK 156256B
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- friction
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Classifications
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H12/00—Towers; Masts or poles; Chimney stacks; Water-towers; Methods of erecting such structures
- E04H12/28—Chimney stacks, e.g. free-standing, or similar ducts
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- E—FIXED CONSTRUCTIONS
- E04—BUILDING
- E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
- E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
- E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
- E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
- E04H9/0215—Bearing, supporting or connecting constructions specially adapted for such buildings involving active or passive dynamic mass damping systems
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01Q—ANTENNAS, i.e. RADIO AERIALS
- H01Q1/00—Details of, or arrangements associated with, antennas
- H01Q1/005—Damping of vibrations; Means for reducing wind-induced forces
Description
! DK 156256 B! DK 156256 B
Opfindelsen vedr0rer et apparat af den i krav l's indled-ning nævnte art. Et sâdant apparat kendes fra det tyske offentliggOrelsesskrift nr. 32 15 428. Det drejer sig om en friktionssvingningsdæmper, i hvilken en pà en pendul-5 stang fastgjort d0dvægt sættes i svingninger af bygnings-værket. Sammenkoblingen mellem d0dvægten og bygningsværket sker via en friktionsvægt, der bevæges af pendulstangen.The invention relates to an apparatus of the kind mentioned in the preamble of claim 1. Such an apparatus is known from German Publication No. 32 15 428. It is a friction vibration damper in which a dead weight fixed on a pendulum rod is placed in vibrations of the structure. The connection between the dead weight and the structure is done via a friction weight that is moved by the shuttle rod.
Med dette kendte apparat, ved hvilken friktionsvægten er 10 opl0st i enkelte pâ hinanden stablede, i forhold til hin-anden forskydelige friktionsplader, lader en igangsætning af dæmpningsapparatet sig opnâ allerede ved smâ bevægelser af bygningsværket. Derved aktiveres der ved tiltagende amplitude for pendulbevægelsen flere og flere friktionspla-15 der, og svarende hertil stiger den optagne energi. Ved dette kendte apparat st0der fagmanden pâ vanskeligheder ved den beregningsmæssige dimensionering af apparatet, da der for friktionsvingningsdæmpere ikke findes en i praksis anvendelig teori.With this known apparatus, in which the weight of the friction is dissolved in single stacked, relative to each other displaceable friction plates, a start of the damping apparatus can be obtained already by small movements of the structure. As a result, with increasing amplitude of the pendulum movement, more and more friction plates are activated, and correspondingly the absorbed energy increases. In this known apparatus, one skilled in the art will encounter difficulties in the computational sizing of the apparatus, as there is no practical application for friction vibration dampers.
2020
Til grund for den foreliggende opfindelse ligger den opga-ve at forbedre det kendte apparat med over hinanden stablede friktionsplader sâledes, at dets dæmpningsvirkning er sâ nojagtigt som muligt tilpasset til bygningsværkets 25 svingninger, sâvel som. at den beregningsmæssige be- skrivelse og dermed dets dimensionering i forhold til det pàgældende bygningsværkK forenkles.The object of the present invention is to improve the known apparatus with overlaid friction plates so that its damping effect is as precisely as possible adapted to the vibrations of the building work, as well as. that the calculation description and thus its dimensioning in relation to the building in question are simplified.
If0lge opfindelsen dimensionerer man for at opfylde formâ-30 let friktionspladerne i en friktionssvingnignsdæmper af den i indledningen nævnte art sâledes, at man kan anvende "den Hartog’ske teori" for to-masse-svingninger med vis-kosdæmpning. Ved at nà dette mâl pà den nedenfor beskrevne mâde er det for f0rste gang muligt ved en svingningsdæmper 35 at realisere, at den optagne energi bliver proportional med kvadratet pâ svingningsamplituden, sâledes som det pà kendt mâde sker i den viste svingningsdæmper. Denne optag-According to the invention, in order to fulfill the purpose of the friction plates in a friction vibration damper of the kind mentioned in the preamble, it is dimensioned so that one can use "Hartog's theory" for two-mass vibrations with viscous damping. By attaining this measure in the manner described below, it is possible for the first time to realize, by a vibration damper 35, that the absorbed energy becomes proportional to the square of the vibration amplitude, as is known in the manner shown in the vibration damper. This recording
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ne energi beregnes med ligningenne energy is calculated with the equation
Wd * n*k*w*x , 5 hvori k er en dæmpningskonstant, w er svingningsimpulsens cyklusfrekvens og x igen svingnings ampli tuden. Den optagne energi svarer if01ge denne ligning til en ellipses ind-hold; den 0ges med kvadratet pâ svingningsamplituden.Wd * n * k * w * x, 5 wherein k is a damping constant, w is the oscillation pulse cycle frequency and x again the oscillation amplitude. According to this equation, the energy absorbed corresponds to the content of an ellipse; it is added by the square of the oscillation amplitude.
10 For at nâ formâlet skal dimensioneringen af friktionspla-derne p£ for i = 1 til n ske under iagttagelse af neden-stâende regler: a) aile friktionsplader p± skal hâve samme pladetykkelse 15 t; friktionskoefficienten mellem de enkelte friktions plader skal være lige stor, b) med en antagen huldiameter dj i den 0verste friktions-plade px tiltager huldiameteren fra den 0verste til 20 den nederste friktionsplade svarende til produktet i d; i = 1, 2, 3 ... n = friktionspladernes 10bende num-mer.10 In order to achieve this, the dimensioning of the friction plates p £ for i = 1 to n must be observed, subject to the following rules: (a) all friction plates p ± must have the same plate thickness 15 t; the coefficient of friction between the individual friction plates must be equal; (b) with an assumed hole diameter dj in the upper friction plate px, the hole diameter from the upper to 20 increases the lower friction plate corresponding to the product in d; i = 1, 2, 3 ... n = number of friction plates 10b.
c) Aftrapningen af friktionspladernes ydre diameter be- 25 régnés ud fra det krav, at den pr svingning optagne energi skal vokse med kvadratet pâ penduludslaget dx. Dette krav er opfyldt, nâr friktionspladen p1 for i = 2 til n hele tiden dimensioneres dobbelt sâ tung sont den 0verste friktionsplade pt. Reglen Gi = 2’Gj^ gæl-30 der. Pâ grund af den forudsat konstante gnidningskoef- ficient mellem de enkelte friktionsplader kan denne betingelse ogsâ formuleres sâledes, at ved aktivering af friktionspladerne fra i = 2 skal der hele tiden indtræde en for0gelse af gnidningskraften: R4 = μ * 2 * Gx = 2*Ra 35c) The step-down of the outer diameter of the friction plates is calculated from the requirement that the energy absorbed per oscillation must grow by the square of the pendulum stroke dx. This requirement is met when the friction plate p1 for i = 2 to n is constantly dimensioned twice as heavy as the upper friction plate pt. The rule Gi = 2'gj2 applies. Due to the assumed constant coefficient of friction between the individual friction plates, this condition can also be formulated so that by activating the friction plates from i = 2, an increase in the frictional force must always occur: R4 = μ * 2 * Gx = 2 * Ra 35
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Bragt pâ en kort formel kommer det for friktionsplader, som har huiler if01ge betlngelse b) an pâ, at aile frik-tionsplader med i st0rre end eller 11g med 2 skal hâve samme gnidningsmodstand, og den skal være den dobbelte af 5 den 0verste friktionsplades gnidningsmodstand.Brought to a short formula, for friction plates having cavities according to condition b), all friction plates having greater than or 11g by 2 must have the same frictional resistance, and must be twice the friction plate friction resistance .
Efter fastlæggelse af friktionspladernes tykkelse, af ar-ten af det for aile friktionspladerne fælles materiale samt af den udvendige diameter Dj pâ den 0verste frik-10 tionsplade px kan en fagmand med den ovenfor angivne sam-menhæng mellem vægten af friktionspladerne udregne de en-kelte friktionspladers mâl. Da friktionspladerne som for-udsat skal være cirkelformede med centrait anbragte, cir-kulære huiler kan vægten beregnes med formlen: 15 π G s'îf't· 4 *(D2-d2), idet det gælder at 2Γ = vægtfylden (N/m3) t = friktionspladetykkelsen (m) 20 D = den udvendige diameter (m) d = huldiameteren (m).After determining the thickness of the friction plates, of the nature of the material common to all the friction plates and of the outer diameter Dj of the upper friction plate px, one skilled in the above relationship between the weight of the friction plates can calculate the individual milling friction plates. Since the friction plates must be circularly shaped with centrait arranged, circular weights, the weight can be calculated by the formula: 15 π G s'îf't · 4 * (D2-d2), where 2Γ = the density (N / m3) t = friction plate thickness (m) 20 D = outside diameter (m) d = hole diameter (m).
En hensigtsmæssig udformning af den 0verste friktionsplade ρχ opnâes, nâr denne plades yderdiameter Dx er mellem fire 25 og tolv gange dens huldiameter d^ og nâr dens huldiameter dx kun er ganske lidt st0rre end pendulstangens diameter i stangens nedre ende, der rager ind i det af friktionspladerne P dannede hulrum.An appropriate design of the upper friction plate ρχ is obtained when the outer diameter Dx of this plate is between four and twelve times its hole diameter d the friction plates P formed voids.
30 Fordi den optagne energi Wd er proportional med kvadratet pâ svingningsamplituden, opnàr man, at en bestemt i byg-ningsværket indf0rt mekanisk svingningsenergi kan blive optaget med væsentligt mindre penduludsving "x" end det er muligt med friktionsdæmpere af hidtil kendt art med lineær 35 proportionalitet mellem den optagne energi og svingningsamplituden "x". Hermed kan man med apparatet if0lge opfin-delsen holde dimensionerne i penduludsvingets retning til-30 Because the absorbed energy Wd is proportional to the square of the oscillation amplitude, it is obtained that a certain mechanical oscillation energy introduced into the building can be absorbed with substantially smaller pendulum vibrations "x" than is possible with friction dampers of the prior art of linear proportionality. between the absorbed energy and the oscillation amplitude "x". In this way, the apparatus according to the invention can keep the dimensions in the direction of the pendulum swing.
4 DK 156256 B4 DK 156256 B
svarende smâ. Forslaget if0lge opfindelsen muligg0r altsâ ikke blot en særligt 0konomisk fremstilling af svingnings-dæmpningsapparatet; dets mindre dimensioner er ogsâ pâ grund af det bedre optiske indtryk meget 0nskværdigt.answering small. Thus, the proposal according to the invention not only allows for a particularly economical manufacture of the vibration damping apparatus; its smaller dimensions are also very desirable due to the better optical impression.
55
Som allerede sagt er den afg0rende fordel til gunst for apparatet if0lge opfindelsen den særligt enkle beregnings-mulighed; det gælder sâvel med hensyn til dimensioneringen af konstruktionsdelene, herunder specielt af friktionspla-10 derne, som med hensyn til dets tilpasning til forholdene i det pâgældende bygningsværk.As already stated, the decisive advantage in favor of the apparatus according to the invention is the particularly simple calculation option; this applies both to the design of the structural parts, in particular of the friction plates, as well as to its adaptation to the conditions of the building in question.
Nedenfor gennemregnes et udformningseksempel pâ en frik-tionsvægt med seks friktionsplader. I forbindelse hermed 15 henvises der til den medf01gende, skematiske illustration af en sâdan udformning vist i tegningen.A design example of a friction weight with six friction plates is calculated below. In connection with this, reference is made to the accompanying schematic illustration of such a design shown in the drawing.
Tegningen viser et pendul 1 i hvilestillingen. Friktions-vægten bestàr af seks friktionsplader px til p6, der aile 20 er udformet som cirkelskiver med tykkelsen t. Den nederste ende 2 af pendulet 1 griber ind i et hulrum 3, som er dan-net af centrait placerede, cirkelrunde huiler i de enkelte friktionsplader. Friktionsvægten hviler pâ en bund 4 i et ikke nærmere vist hus. Bunden 4 kan som vist være plan el-25 1er være tildannet hvælvet svarende til pendulbevægelsen.The drawing shows a pendulum 1 in the rest position. The friction weight consists of six friction plates px to p6, all of which 20 are formed as circular discs of thickness t. The lower end 2 of the pendulum 1 engages in a cavity 3, which is formed of centrally placed, circular cavities in the individual friction plates. The friction weight rests on a bottom 4 of a housing not shown. The bottom 4 may, as shown, be planar or 25 formed of the vault corresponding to the pendulum movement.
Dens overflade udg0r gnidningsfladen for den af pladerne px til p6 sammensatte friktionsvægt, som bliver forskudt af pendulstangens 7 nederste ende 2 under pendulets 1 be-vægelse, idet i forhold til den i tegningen viste hvile-30 stilling f0rst den 0verst© friktionsplade px og derefter, i afhængighed af svingningsamplituden, i rækkef01ge efter hverandre friktionspladerne p2 til p6 bliver sat i bevæ-gelse indtil - ved bygningsværkets st0rste udsvingning -friktionsvægten bliver bevæget i sin helhed.Its surface is the friction surface of the friction weight composed of the plates px to p6 which is displaced by the lower end 2 of the pendulum rod 7 during the movement of the pendulum 1, with respect to the rest position shown in the drawing first the friction plate px and then , depending on the oscillation amplitude, in succession, the friction plates p2 to p6 are moved until - at the largest oscillation of the structure - the friction weight is moved in its entirety.
Pendulet 1 er ophængt i et antydningsvis illustreret kug-leled 5 pâ enden af en kragstiver 6, som, hvilket ikke er 35The pendulum 1 is suspended in a suggestively illustrated ball joint 5 at the end of a collet strut 6 which, which is not 35
5 DK 156256 B5 DK 156256 B
illustreret nærmere, er fast forbundet med et bygnings-værk.illustrated in more detail, is firmly associated with a building work.
Pà pendulstangen 7 er der ophængt en svingmasse 8, som ait 5 efter bygningsværket er mellem 100 og 700 kg. I forhold hertil er den af flere friktionsplader px til p6 sammen-satte friktionsvægt betydeligt mindre. Udtrykt i tal udg0r den mindre end 10% af svingmassen.On the shuttle rod 7, a swing mass 8 is hung, which is 5 after the construction is between 100 and 700 kg. In comparison, the friction weight of several friction plates px to p6 is considerably less. In terms of numbers, it makes up less than 10% of the swing mass.
10 De enkelte friktionsplader px til p6 er tildannede med centrait placerede huiler med forskellig st0rrelse; huldi-ameteren d2 i pladen px er valgt sàledes, at den nedre en-de 2 af pendulstangen 7 omsluttes snævert. De enkelte hul-diametre er valgt pâ f01gende mâde: 15The individual friction plates px to p6 are formed with centrally placed weights of different sizes; the hole diameter d2 in the plate px is selected such that the lower end 2 of the shaft rod 7 is tightly enclosed. The individual hole diameters are selected as follows: 15
Friktionsplade px : huldiameter dx = d Friktionsplade p2 : huldiameter d2 = 2d Friktionsplade p3 : huldiameter d3 = 3d Friktionsplade p4 : huldiameter d4 = 4d 20 Friktionsplade p5 : huldiameter d5 = 5d Friktionsplade p6 : huldiameter d6 = 6dFriction plate px: hole diameter dx = d Friction plate p2: hole diameter d2 = 2d Friction plate p3: hole diameter d3 = 3d Friction plate p4: hole diameter d4 = 4d 20 Friction plate p5: hole diameter d5 = 5d Friction plate p6: hole diameter d6
Til beregning af aftrapningen af den udvendige diameter i et konkret udformningseksempel forudsættes det, at den 0-25 verste plade Pi har en udvendig diameter Dx, som er seks-gange huldiameteren dx, hvorfor det gælder at:To calculate the step-down of the outside diameter in a concrete design example, it is assumed that the 0-25 worst plate Pi has an outside diameter Dx, which is six times the hole diameter dx, which is why:
Dx = 6'dj; 30 Yderligere antages det, at f01gende talværdier er gælden-de:Dx = 6'dj; Further, it is assumed that the following numerical values are applicable:
kg Nkg N
Vægtfylde 2Γ = 8000 _ = 80 000 _; 35 m3 m3Density 2Γ = 8000 _ = 80,000 _; 35 m3 m3
Huldiameter d = 20 mm = 0,02 m;Hole diameter d = 20 mm = 0.02 m;
, DK 156256B, DK 156256B
66
Friktionspladetykkelse t = 10 mm = 0,01 m;Friction plate thickness t = 10 mm = 0.01 m;
If01ge ligningen G- (I) 5 fâr man med Dx = 6dt for den 0verste friktionsplade atAccording to Equation G- (I) 5, with Dx = 6dt for the upper friction plate,
P1 : Il = 80 000 0,01·£.0Ρ22 (62-12) = 8,79NP1: Il = 80 000 0.01 · £ .0Ρ22 (62-12) = 8.79N
ΡΊ = 6»0,02 = 0,12 m 10ΡΊ = 6 »0.02 = 0.12 m 10
Efter reglen if0lge krav 2 er vægten af hver af aile 0vri-ge friktionsplader for i st0rre end eller lig med 2 dobbelt sâ stor som vægten af friktionspladen Gt, nâr man ogsâ forudsætter samme gnidningskoefficient for aile frik-15 tionspladerne.According to the rule of claim 2, the weight of each of the free friction plates for greater than or equal to 2 is twice the weight of the friction plate Gt, when the same friction coefficient for all the friction plates is also assumed.
Altsà gælder: G± = 2*Gj = 17,58 N for i st0rre end eller lig med 2; 20 Indsætter man denne værdi i ovennævnte ligning (X) for pladevægten, sâ fâr man: D.!-(1d)' «lu,,; 25 Df «τ/6*·-™* 1 r r-t-f for Gt = 2’Gj^ = konstant = 17,58 og i = 2 til 6 fremkommer f01gende værdier for 30 D, =l/17,5? Ψ *<2 °-02)i'; D2 = 0,3¾ m; pâ samme mâde udregnes den udvendige diameter pâ de 0vrige 35Thus: G ± = 2 * Gj = 17.58 N for greater than or equal to 2; 20 If you add this value in the above equation (X) to the plate weight, you get: D. - (1d) '' lu ,,; 25 Df «τ / 6 * · - ™ * 1 r r-t-f for Gt = 2'Gj ^ = constant = 17.58 and i = 2 to 6, the following values for 30 D = = 17.5 appear? Ψ * <2 ° -02) i '; D2 = 0.3¾ m; in the same way, the outside diameter of the other 35 is calculated
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friktionsplader; som résultat gælder for aile friktions-pladerne:friction plates; as a result apply to all the friction plates:
djn . Djii GtNdjn. Djii GtN
5 px: 0,02 0,120 8,79 p2: 0,04 0,172 17,58 p3: 0,06 0,178 17,58 p4: 0,08 0,185 17,58 p5: 0,10 0,195 17,58 10 p6: 0,12 0,206 17,585 px: 0.02 0.120 8.79 p2: 0.04 0.172 17.58 p3: 0.06 0.178 17.58 p4: 0.08 0.185 17.58 p5: 0.10 0.195 17.58 10 p6: 0 , 12 0.206 17.58
Nedenfor eftervises nu matematisk den kvadratiske afhæn-gighed mellem den optagne energi og svingningsamplituden x = n*d.The square dependence between the absorbed energy and the oscillation amplitude x = n * d is now mathematically shown below.
1515
Med udgangspunkt i den allerede forklarede retvinklede hysteresesl0jfe ved frlktionsdæmpning fâr man nedenstâende firkantindhold ved bevægelsen fra 1, 2, 3 o.s.v. til n friktionsplader: 20 n = 1: Wdl = l*2*d·!*! n = 2: Wd2 = l*2*d*R2 + 2*2^*^ n = 3: Wd3 = l*2*d*R3 + 2·2*ά^2 + 3*2*d*R1 25 med 10bende variabel i - 1 til n n Σ i*(2d R ) = y ,=a n+H' ‘ wd (II) 30On the basis of the already explained right-angled hysteresis loop for fractional damping, the following square content is obtained for the movement from 1, 2, 3, etc. to n friction plates: 20 n = 1: Wdl = l * 2 * d ·! *! n = 2: Wd2 = l * 2 * d * R2 + 2 * 2 ^ * ^ n = 3: Wd3 = l * 2 * d * R3 + 2 · 2 * ά ^ 2 + 3 * 2 * d * R1 25 with 10bend variable i - 1 to nn Σ i * (2d R) = y, = a n + H '' wd (II) 30
Denne ligning tager hensyn til de forskellige friktionsplader s forskellige forskydningsveje. Den 0verste frik-tionsplade px bliver altid bevæget. Dens huldiameter sæt-tes lig med pendulendens 2 diameter. Den anden friktions-35 plade har en huldiameter 2d og altsâ en hulfrigang d. Be-væger pendulenden sig indenfor denne hulfrigang, sâ bliver kun den f0rste friktionsplade px aktiveret; herved udg0rThis equation takes into account the different shear paths of the different friction plates. The upper friction plate px is always moved. Its hole diameter is set equal to the diameter of the pendulum 2. The second friction plate has a hole diameter 2d and thus a hole release d. If the pendulum moves within this hole release, then only the first friction plate px is activated; hereby constitutes
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firkantfladen for en hel svingningscyklus Wdl = 2‘d‘Rj^the square surface for an entire oscillation cycle Wdl = 2'd'Rj ^
Ved yderligere forskydning bliver ogsâ friktionspladen p2 med R2 aktiveret og genneml0ber herunder den ekstra sving-ningsvej d. F0rst ved st0rre penduludslag end 2d bliver 5 den tredie friktionsplade p3 aktiveret, der med en huldia-meter pâ 3d tillader en pendulfrigang pâ 2d uden selv at komme i bevægelse. Disse bevægelsesfaser genneml0ber hver svingningscyklus en gang i begge svingningsretninger, idet friktionspladerne hele tiden bliver aktiveret i den samme 10 rækkef01ge efter hverandre.Upon further displacement, the friction plate p2 with R2 is also activated and traverses including the extra pivot path d. get moving. These phases of movement go through each oscillation cycle once in both oscillation directions, with the friction plates constantly being activated in the same order in succession.
If01ge krav 1 gælder:According to claim 1, the following applies:
Rt = 2R2 = konstant for i st0rre end eller lig 2.Rt = 2R2 = constant for greater than or equal to 2.
1515
Derfor fèr man fra ligning (II) for for - 20 n=l;i=l : Wdl = 2 d R1 1 n=2;i=2 : Wd2=l 2d R2 + 2 2d Rx = 2 d Rt 4 n=3;i=l, 2, 3,: Wd3=l 2d R3 + 2 2d R2 + 3 2d R2 = 2 d Rx 9 man erkender uden videre afhængigheden af kvadratet pâ n; 25 der gælder altsâ'den enkle sammenhæng:Therefore, from equation (II), for - 20 n = l; i = l: Wdl = 2 d R1 1 n = 2; i = 2: Wd2 = l 2d R2 + 2 2d Rx = 2 d Rt 4 n = 3; i = l, 2, 3,: Wd3 = l 2d R3 + 2 2d R2 + 3 2d R2 = 2 d Rx 9 one recognizes the dependence of the square on n; 25 thus applies to the simple context:
Wdn = 2ά^χ*η idet afhængigheden mellem gnidningskraften og vægten er 30 givet med &i = P‘ex*Wdn = 2ά ^ χ * η where the dependence between the frictional force and the weight is given by & i = P'ex *
Claims (3)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3402449 | 1984-01-25 | ||
| DE3402449A DE3402449C2 (en) | 1984-01-25 | 1984-01-25 | Device for vibration damping on tower-like structures such as chimneys, transmitter masts or the like. |
Publications (4)
| Publication Number | Publication Date |
|---|---|
| DK613684D0 DK613684D0 (en) | 1984-12-20 |
| DK613684A DK613684A (en) | 1985-07-26 |
| DK156256B true DK156256B (en) | 1989-07-17 |
| DK156256C DK156256C (en) | 1989-12-04 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK613684A DK156256C (en) | 1984-01-25 | 1984-12-20 | Apparatus for vibration suppression of long-lasting buildings, such as chimneys, transmitters or similar elongated structures |
Country Status (4)
| Country | Link |
|---|---|
| AT (1) | AT385310B (en) |
| DE (1) | DE3402449C2 (en) |
| DK (1) | DK156256C (en) |
| GB (1) | GB2153463B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3717460A1 (en) * | 1986-11-03 | 1988-05-19 | Teutsch Rudolf | DEVICE AND METHOD FOR VIBRATING ELEMENTS OF VIBRATION LABELED BODIES |
| DE4305132C1 (en) * | 1993-02-19 | 1994-04-21 | Uwe E Dr Dorka | Friction damper for securing support structure against dynamic effects - has superimposed friction plates contacting surfaces which are connected to friction damper connections |
| KR20100114016A (en) | 2007-11-28 | 2010-10-22 | 베스타스 윈드 시스템스 에이/에스 | Method for damping oscillations in a wind turbine |
| DE102012020851A1 (en) | 2012-10-24 | 2014-04-24 | Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. | System for connecting a first component and a second component to form a rigid frame corner |
| US11078890B2 (en) | 2018-05-22 | 2021-08-03 | Engiso Aps | Oscillating damper for damping tower harmonics |
| US11560878B2 (en) * | 2018-06-29 | 2023-01-24 | Vestas Wind Systems A/S | Damper unit for a tower structure |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3215428C2 (en) * | 1982-04-24 | 1984-05-24 | Friedrich Maurer Söhne GmbH & Co KG, 8000 München | Device for vibration damping on tower-like structures such as chimneys, transmitter masts or the like. |
-
1984
- 1984-01-25 DE DE3402449A patent/DE3402449C2/en not_active Expired
- 1984-12-20 DK DK613684A patent/DK156256C/en not_active IP Right Cessation
- 1984-12-21 AT AT0405584A patent/AT385310B/en not_active IP Right Cessation
-
1985
- 1985-01-24 GB GB08501815A patent/GB2153463B/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| AT385310B (en) | 1988-03-25 |
| DE3402449A1 (en) | 1985-08-01 |
| DK613684D0 (en) | 1984-12-20 |
| DE3402449C2 (en) | 1986-04-03 |
| DK156256C (en) | 1989-12-04 |
| GB2153463B (en) | 1987-09-09 |
| ATA405584A (en) | 1987-08-15 |
| GB2153463A (en) | 1985-08-21 |
| GB8501815D0 (en) | 1985-02-27 |
| DK613684A (en) | 1985-07-26 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PBP | Patent lapsed |