EP3548675A1 - Tuned dynamic damper and method for reducing the amplitude of oscillations - Google Patents
Tuned dynamic damper and method for reducing the amplitude of oscillationsInfo
- Publication number
- EP3548675A1 EP3548675A1 EP17807865.5A EP17807865A EP3548675A1 EP 3548675 A1 EP3548675 A1 EP 3548675A1 EP 17807865 A EP17807865 A EP 17807865A EP 3548675 A1 EP3548675 A1 EP 3548675A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- inertial mass
- frame
- dynamic damper
- relative
- rotation
- 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.)
- Withdrawn
Links
Classifications
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
- F16F7/1022—Vibration-dampers; Shock-absorbers using inertia effect the linear oscillation movement being converted into a rotational movement of the inertia member, e.g. using a pivoted mass
Definitions
- the present invention relates to a tuned dynamic damper (also called TMD, for "Tuned Mass Damper” in English).
- TMD tuned dynamic damper
- Such dampers are used to attenuate the vibrations of a structure in a restricted range of frequencies around the resonant frequency of the structure.
- These systems operate on the principle of transfer cycles between kinetic and potential energies, and dissipation, particularly viscous, of the kinetic energy at each cycle.
- Some such as that disclosed in the publication CN 205153175, implement a first inertial mass, mobile in translation, and a second inertial mass rotatable about a fixed axis of rotation, and whose rotational movement is controlled by a rack moving with the first inertial mass.
- Such dampers are limited to the damping of vertical vibrations.
- Pendulum dampers are also known.
- Such dampers comprise an inertial mass connected by suspension lines to a fixed frame connected to the structure whose vibration is sought to dampen, and a damping system for oscillations.
- Examples of pendular dampers are described in CN204458973U, CN103132628A, CN202954450U.
- US 2013/0326969 discloses a pendulum damper in which the damping of the pendulum movement of the inertial mass is obtained by electromagnetic brakes with induced currents, in order to generate electricity.
- the lines are connected to the fixed frame by hinges configured to rotate armature disks subjected to a magnetic field.
- the armature disks are of very low inertia and participate negligibly in the accumulation of kinetic energy of rotation, compared to the kinetic energy generated by the mass performing the pendulum movement.
- EP 474269 discloses a dynamic damper comprising an inertial mass supported by two parallel rods which drive it in displacement parallel to itself, without rotation on itself relative to the frame. To increase the kinetic energy, one must increase the mass with the disadvantage of having to mechanically reinforce the rods, which increases the cost and bulk of the damper.
- the present invention thus aims to further improve the tuned dynamic dampers and more particularly the pendulum dampers.
- the invention achieves this through dynamic damping tuned pendulum, comprising:
- An inertial mass drive system configured to transform a variation of the angle of at least one line relative to the moving frame or the fixed frame in a relative movement of the inertial mass relative to the frame that carries it.
- the relative movement of the inertial mass relative to the frame which carries it is preferably a rotational movement on itself.
- the invention makes it possible to increase the overall kinetic energy by adding to the kinetic energy related to the movement of the pendulum, that of the movement of the inertial mass relative to the frame which carries it, in particular that of rotation of the inertial mass on it. even.
- the rotational kinetic energy can be increased without having to increase the mass and bulk of the damper.
- the orientation of the inertial mass relative to the frame may change over time relative to the frame due to its rotation on itself.
- the inertial mass can turn on itself over more than 180 °, better for more than 360 ° around a specific axis of rotation during the operation of the shock absorber.
- the inertial mass is carried by the movable frame.
- the drive system advantageously comprises a gear reduction mechanism.
- a small angular variation of the lines can be converted into a rotational movement of the inertial mass on itself significant.
- the drive system may comprise a driving gear, guided in rotation relative to the movable frame, and which is hung a hanger.
- This driving gear can mesh with a driven gear, guided in rotation by the movable frame and rotating with the inertial mass.
- the drive system comprises at least one rack.
- the latter is for example hooked at its ends to the lines.
- the drive system may comprise a pinion rotating with the inertial mass and meshing on the rack.
- the damper comprises a pinion meshing on the rack and driving through a suitable mechanism, including a bevel gear, the inertial mass, the latter preferably having a axis of vertical rotation when the shock absorber is at rest.
- the damper may include in particular two parallel racks and a pair of gears meshing on these racks and coupled to the same drive shaft of the inertial mass.
- the mobile frame comprises a first and a second frame, the lines being hooked to the first frame and being coupled to the second frame so that an angular movement of the lines relative to the vertical s' accompanied by a displacement of the second frame relative to the first.
- the inertial mass is connected to the chassis so that the relative movement of the chassis relative to each other is accompanied by a rotational movement of the inertial mass relative to the chassis.
- the inertial mass can be connected by ball joints to the chassis.
- the damping movements of the inertial mass as well as those of the mobile frame can be carried out in various ways, seeking or not to recover the kinetic energy to produce electricity.
- the tuned dynamic damper comprises one or more viscous dampers, which can be arranged in various ways depending on the structure of the damper.
- the above-mentioned lower and upper frames are connected by viscous dampers.
- the tuned dynamic damper comprises at least one friction or induction brake.
- the damper may be unidirectional but preferably it is bidirectional. It may comprise at least two inertial masses, rotating about respective axes of rotation perpendicular to each other, or alternatively axial co and oriented vertically when the damper is at rest.
- the tuned dynamic damper has four flywheels, the diametrically opposed flywheels rotating about parallel axes of rotation.
- the weight of the inertial mass may be such that the ratio ECR / ECT of the nominal kinetic energy of the inertial mass rotating on itself at the nominal kinetic energy in translation is between 0.4 and 100, better between 0.4 and 10.
- the tuned dynamic damper is normally intended to operate for relatively frequent wind, seismic or other loads, for which an attempt is made to maintain a given comfort level, or even to maintain a stress level below a certain limit.
- the tuned dynamic damper can be stopped because of exceptional wind, seismic or other conditions, which are rare.
- the maximum stress can correspond to a limit load before an abutment against a protection system relating to accidental solicitations.
- a ratio of from 0.4 to 10 is preferred for large masses, typically greater than 3 kg.
- the inertial mass may be greater than or equal to 10 weight 2 kg, more preferably 5.10 to 2 kg, most preferably to 10 3 kg.
- the invention further relates, in another aspect, a civil engineering work, including a tower or a walkway, equipped with a damper according to the invention, as defined above.
- the invention also relates to a method for reducing the amplitude of the oscillations of a civil engineering structure, in particular a tower or a bridge, using a damper as defined above, in which it is possible to the mobile frame to oscillate in a pendular manner so as to reduce the amplitude of the oscillations of the structure.
- FIG. 1 schematically and partially shows, in perspective, an exemplary dynamic damper according to the invention
- FIGS. 2 to 4 are views similar to FIG. 1 of variant embodiments
- FIG. 5 represents a detail of the drive system of the flywheels of the damper of FIG. 4,
- FIG. 6 is a view similar to FIG. 1 of another variant embodiment.
- FIG. 7 shows a detail of the embodiment of the damper of Figure 6.
- a tuned dynamic damper 1 according to the invention, comprising a set of lines 10, four in the example considered.
- the lines 10 are hingedly hinged at their upper end 11 to a fixed frame 2 of the structure equipped with the damper, for example a house tower and / or high office. They support at their lower end 12 a mobile frame 20 which carries four inertial masses 30 in the form of flywheels, each rotatable on themselves relative to the mobile frame 20.
- the damper 1 comprises two flywheels 30a diametrically opposed, rotating about axes of rotation X parallel to each other, and two other flywheels 30b also diametrically opposed and rotating about axes of rotation. Y rotation parallel to each other and perpendicular to the X axis.
- the movable frame 20 comprises beams 21 which extend between the flywheels 30 and which support bearings that rotate the shafts rotating with the corresponding flywheels 30.
- each shaft which rotates a corresponding flywheel on the frame 20 carries a pinion 33.
- Each of the lines 10 is connected at its lower end 12 to a toothed wheel 26, the articulation of the suspension on this wheel being eccentric with respect to the axis of rotation of the wheel.
- Each gear 26 meshes with a corresponding pinion 33.
- the pendular oscillation of the mobile frame 20 with the flywheels 30 is accompanied by a variation of the angle of the longitudinal axis of the lines 10 relative to the mobile frame 20 and a rotation of a or more of the wheels 26 relative to the frame 20. This rotation drives that of the corresponding flywheel through the pinion 33 which meshes with the wheel 26.
- the oscillation of the damper is therefore accompanied by a rotation of the flywheels 30 and an accumulation of kinetic energy in rotation, in addition to that related to the swinging oscillation movement.
- the wheels 26 and the corresponding pinions 33 can be produced so as to obtain a reduction factor greater than 1 in order to increase the speed of rotation of the flywheels and the kinetic energy of rotation.
- Each flywheel 30 may be associated, as illustrated, with a braking means of the viscous type of its rotation, that is to say exerting a braking torque which is all the more important that the speed of rotation is high.
- each flywheel is associated with an induction brake disc 40.
- the movable frame 20 carries a single inertial mass 30 in the form of a flywheel, rotating about an axis of rotation X.
- the flywheel 30 rotates with two pinions 33 arranged at each of its axial ends, which each mesh with a corresponding rack 50 extending between two lines 10 and coupled thereto by means of fasteners 52.
- a pendulum oscillation of the damper 1 in a plane perpendicular to the axis X is accompanied by a variation of the angle of the lines 10 relative to the mobile frame and a movement of the racks 50 relative to the frame, which causes rotation of the flywheel 30 around the X axis.
- the flywheel 30 may be equipped with a brake disk, for example inductive or by friction, so as to dissipate the kinetic energy of rotation.
- the movable frame 20 can be made with each side of the flywheel 30 two spaced parallel beams 61 and 62, between which is disposed the pinion 33 corresponding.
- FIG. 3 is bidirectional, comprising a mobile frame 20 comprising a frame inside which four inertial masses 30 are arranged in the form of flywheels, each associated with a pinion 33 and with a rack 50, these the latter being arranged respectively along the four sides of the frame of the mobile frame 20.
- the latter can comprise as illustrated two cross beams 65, joined in their middle and being connected respectively to the four corners of the frame of the frame 20.
- the flywheels 30 may have, as illustrated, each a generally frustoconical shape, converging towards the center of the frame 20.
- Each wheel 30 may be equipped with a brake 40, for example inductive or friction.
- the damper 1 comprises two flywheels 30 which are co axial and which rotate about an axis of rotation Z which is vertical when the damper is at rest.
- the flywheel drive system 30 comprises, as in the embodiment of FIG. 3, four racks 50 which each connect two adjacent lines 10, being coupled thereto, so that an oscillation of the mobile frame 20 accompanied by a movement of the racks 50 parallel to the corresponding sides of the frame 20.
- the movement of the racks 50 is transmitted to the flywheels 30 by pinions 33.
- Two opposite gears are connected by a shaft 70a and the other two by a another tree 70b crossing the first.
- the pinions 33 are guided in rotation by the frame 20 and rotate, as can be seen in Figure 5, with the shafts 70a and 70b.
- Each shaft 70a or 70b carries a corresponding bevel gear 71 which meshes with a bevel gear 72 rotating with the corresponding flywheel 30, so that a rotation of the gears 33 on themselves is accompanied by a rotation of the corresponding flywheel 30 about the axis of rotation Z.
- the tuned dynamic damper 1 of FIG. 4 is thus bidirectional.
- FIGS. 6 and 7 illustrate an alternative embodiment of the tuned dynamic damping device 1 without gearing to increase the angular movement of the lines 10 relative to the mobile frame 20.
- the mobile frame 20 comprises a lower frame 80 and an upper frame 81 of similar shapes, comprising an outer frame of polygonal shape, in this case square, and an X-shaped structure with two beams 85 crossing each other. their middle 86 and connecting at their ends to the corners of the frame 84.
- the frames 80 and 81 are interconnected by viscous dampers 83 which are for example arranged at mid-length sides of each frame.
- Each line 10 is connected by its lower end 12 hingedly to the lower frame 80 and passes through the upper frame 81 in favor of a corresponding opening 86, with a small clearance.
- the variation of the angle of the lines relative to the lower frame 80 is accompanied by a displacement of the upper frame 81 relative to the lower frame 80.
- the central portions 86 of the chassis 80 and 81 thus have a misalignment which is variable during the oscillation of the mobile frame 20.
- the tuned dynamic damper 1 comprises a single inertial mass 30 which comprises four blocks 90 of general pyramidal shape converging towards the center, connected by two crosses 92 spaced vertically. Crosses 92 are connected by a shaft 95 of vertical Z axis when the damper 1 is at rest.
- the shaft 95 comprises ball joints 97 which are respectively engaged in the central portions 86 of the upper frame 81 and lower 80.
- the relative movement of the upper frame 81 relative to the lower frame 80 is accompanied by a tilting of the shaft 95 and a rotation of the blocks 90.
- the latter are part of the triangles formed by the X structures of the upper and lower frames.
- the inertial mass and the mechanism for transmitting the angular variation of a line relative to the vertical to the inertial mass can be made differently to cause it to rotate on itself.
Landscapes
- Engineering & Computer Science (AREA)
- Architecture (AREA)
- General Engineering & Computer Science (AREA)
- Business, Economics & Management (AREA)
- Emergency Management (AREA)
- Environmental & Geological Engineering (AREA)
- Mechanical Engineering (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Buildings Adapted To Withstand Abnormal External Influences (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1661862A FR3059747B1 (en) | 2016-12-02 | 2016-12-02 | TUNED DYNAMIC SHOCK ABSORBER |
PCT/EP2017/081069 WO2018100109A1 (en) | 2016-12-02 | 2017-11-30 | Tuned dynamic damper and method for reducing the amplitude of oscillations |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3548675A1 true EP3548675A1 (en) | 2019-10-09 |
Family
ID=58162804
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17807865.5A Withdrawn EP3548675A1 (en) | 2016-12-02 | 2017-11-30 | Tuned dynamic damper and method for reducing the amplitude of oscillations |
Country Status (7)
Country | Link |
---|---|
US (1) | US20190284800A1 (en) |
EP (1) | EP3548675A1 (en) |
KR (1) | KR20190089972A (en) |
CA (1) | CA3045712A1 (en) |
FR (1) | FR3059747B1 (en) |
RU (1) | RU2719844C1 (en) |
WO (1) | WO2018100109A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016122999B4 (en) * | 2016-11-29 | 2019-01-31 | Burkhard Dahl | Compact spatial ellipsoid mass pendulum |
CN112900672B (en) * | 2021-01-29 | 2022-01-07 | 华中科技大学 | Rolling mass tuned damper improved based on inertia amplification mechanism |
KR102643581B1 (en) * | 2021-07-01 | 2024-03-05 | (주)티이솔루션 | pendulum type vibration control device |
CN113863526B (en) * | 2021-09-18 | 2022-11-25 | 湖南省潇振工程科技有限公司 | Pendulum type inerter tuned mass eddy current damper |
Family Cites Families (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US989958A (en) | 1909-10-30 | 1911-04-18 | Hermann Frahm | Device for damping vibrations of bodies. |
SU779533A1 (en) * | 1978-12-06 | 1980-11-15 | Ордена Трудового Красного Знамени Центральный Научно-Исследовательский И Проектный Институт Строительных Металлоконструкций | Dynamic damper of construction vibrations |
SU1024567A1 (en) * | 1982-01-04 | 1983-06-23 | Ордена Трудового Красного Знамени Центральный Научно-Исследовательский И Проектный Институт Строительных Металлоконструкций "Цниипроектстальконструкция" | Dynamic oscillation damper |
JPS58225241A (en) * | 1982-06-21 | 1983-12-27 | Chiyoda Chem Eng & Constr Co Ltd | Vibration damping apparatus for structure |
SU1544915A1 (en) * | 1988-05-19 | 1990-02-23 | Центральный научно-исследовательский и проектный институт строительных металлоконструкций им.Н.П.Мельникова | Dynamic oscillation damper of pendulum type |
JP2715123B2 (en) * | 1988-11-30 | 1998-02-18 | カヤバ工業株式会社 | Damping device |
JP2760357B2 (en) * | 1989-01-31 | 1998-05-28 | 株式会社竹中工務店 | Building vibration control device |
JP2790185B2 (en) * | 1989-02-15 | 1998-08-27 | 辰治 石丸 | Seismic isolation / vibration control mechanism for a structure with a differential double lever mechanism |
NZ238798A (en) * | 1990-08-30 | 1993-11-25 | Mitsubishi Heavy Ind Ltd | Low height long period pendulum damping equipment for tall buildings |
RU2096565C1 (en) * | 1996-02-12 | 1997-11-20 | Акционерное общество закрытого типа Центральный научно-исследовательский и проектный институт строительных металлоконструкций им.Н.П.Мельникова | Dynamic oscillation dampener |
JPH10252821A (en) * | 1997-03-18 | 1998-09-22 | Mitsui Eng & Shipbuild Co Ltd | Hybrid vibration damping device |
DK174404B1 (en) * | 1998-05-29 | 2003-02-17 | Neg Micon As | Wind turbine with vibration damper |
JP2000074135A (en) * | 1998-08-28 | 2000-03-07 | Daiwa House Ind Co Ltd | Vibration control structure and vibration control device |
DE102007024431A1 (en) * | 2007-05-25 | 2008-11-27 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Device for damping vibrations in vibrating device, particularly in servo-hydraulic testing device such as hydro-pulser, has damper mass, which is charged with vibrations of vibrating device by receiving console |
US20110030471A1 (en) * | 2009-08-07 | 2011-02-10 | Teruo Maeda | Oscillation control device |
EP2681463B1 (en) | 2011-03-04 | 2015-05-06 | Moog Inc. | Structural damping system and method |
CN202954450U (en) | 2012-12-05 | 2013-05-29 | 山东电力工程咨询院有限公司 | Bidirectional horizontal adjustable damping control device |
CN203034632U (en) | 2012-12-26 | 2013-07-03 | 清华大学 | Rolling tuned mass damper |
CN103132628B (en) | 2013-03-13 | 2015-04-08 | 上海材料研究所 | Pendulum eddy current tuning mass damper device |
CN203499047U (en) * | 2013-09-10 | 2014-03-26 | 隔而固(青岛)振动控制有限公司 | Low-frequency pendulum type tuned mass damper |
CN103603917B (en) * | 2013-11-18 | 2015-12-09 | 大连理工大学 | A kind of magnetorheological suspended mass pendulum damper |
CN204458973U (en) | 2015-02-09 | 2015-07-08 | 宁波大学 | A kind of simple liquid damping TMD |
CN205153175U (en) | 2015-11-24 | 2016-04-13 | 华北水利水电大学 | Harmonious mass damper frequency regulation arrangement |
US11078890B2 (en) * | 2018-05-22 | 2021-08-03 | Engiso Aps | Oscillating damper for damping tower harmonics |
-
2016
- 2016-12-02 FR FR1661862A patent/FR3059747B1/en not_active Expired - Fee Related
-
2017
- 2017-11-30 RU RU2019116837A patent/RU2719844C1/en active
- 2017-11-30 US US16/465,771 patent/US20190284800A1/en not_active Abandoned
- 2017-11-30 CA CA3045712A patent/CA3045712A1/en not_active Abandoned
- 2017-11-30 WO PCT/EP2017/081069 patent/WO2018100109A1/en unknown
- 2017-11-30 KR KR1020197019081A patent/KR20190089972A/en not_active Application Discontinuation
- 2017-11-30 EP EP17807865.5A patent/EP3548675A1/en not_active Withdrawn
Also Published As
Publication number | Publication date |
---|---|
CA3045712A1 (en) | 2018-06-07 |
RU2719844C1 (en) | 2020-04-23 |
KR20190089972A (en) | 2019-07-31 |
FR3059747B1 (en) | 2020-03-27 |
FR3059747A1 (en) | 2018-06-08 |
WO2018100109A1 (en) | 2018-06-07 |
US20190284800A1 (en) | 2019-09-19 |
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