WO2022019923A1 - Absorbeur d'énergie passive rotatif hybride - Google Patents

Absorbeur d'énergie passive rotatif hybride Download PDF

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Publication number
WO2022019923A1
WO2022019923A1 PCT/US2020/043603 US2020043603W WO2022019923A1 WO 2022019923 A1 WO2022019923 A1 WO 2022019923A1 US 2020043603 W US2020043603 W US 2020043603W WO 2022019923 A1 WO2022019923 A1 WO 2022019923A1
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WO
WIPO (PCT)
Prior art keywords
axle
hybrid
energy absorber
pea
passive energy
Prior art date
Application number
PCT/US2020/043603
Other languages
English (en)
Inventor
Maor Farid
Original Assignee
Massachusetts Institute Of Technology
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 Massachusetts Institute Of Technology filed Critical Massachusetts Institute Of Technology
Priority to PCT/US2020/043603 priority Critical patent/WO2022019923A1/fr
Publication of WO2022019923A1 publication Critical patent/WO2022019923A1/fr

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Classifications

    • 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 energy transfer devices, and in particular to a passive oscillating and rotating energy absorber.
  • TMDs tuned mass dampers
  • NESs nonlinear energy sinks
  • a TMD becomes ineffective since a TMD requires large spaces or loses its linearity due to large-amplitude oscillations.
  • NES have essential nonlinearities that allows them to adapt their oscillations frequency and hence can be effective for a broader frequency range.
  • their nonlinear and more sophisticated design allows NES to be more compact with respect to the TMDs.
  • the NES designs suffer from a common shortcoming of effectiveness for merely high intensity vibration. When the PS perform small amplitude oscillations, the nonlinearity of the NES cannot come into play and as a result the NES does not perform significant oscillations and absorb the undesired energy from the PS into the NES.
  • the rotational NES can rotate in the plane of excitation around a vertical axis.
  • the NES performs well when the PS performs intensive vibration and manages to mitigate its vibration.
  • the rotational mass does not manage to perform rotations and hence only a low portion of the energy is absorbed into the rotational PEA. Therefore, there is a need in the industry to address one or more of these shortcomings.
  • Embodiments of the present invention provide a hybrid rotational passive energy absorber.
  • the present invention is directed to hybrid rotational passive energy absorber configured to mitigate effects of a load on an attached system.
  • An axle is anchored to a housing at a first axle end and a second axle end.
  • a free swinging weighted arm includes a beam having a length L, a pivot portion disposed at a first end of the beam, and an internal mass at a second end of the beam.
  • a bearing rotatably connects the pivot portion to the axle. The bearing is configured to provide smooth motion of the weighted arm around an axis of the axle in a rotation and/or oscillation plane orthogonal to the axis.
  • FIG. 1 A is a schematic drawing showing an external view of a first embodiment of a hybrid-rotational passive energy absorber (HR-PEA).
  • HR-PEA hybrid-rotational passive energy absorber
  • FIG. IB is an alternative view of FIG. IB having a partially transparent housing.
  • FIG. 2 is a schematic drawing detailing the functional components of the HR-PEA of FIG. IB.
  • FIG. 3 A is a schematic diagram of the HR-PEA of FIG. IB in oscillatory mode.
  • FIG. 3B is a schematic diagram of the HR-PEA of FIG. IB in rotation mode.
  • FIG. 4 is a schematic diagram of a model used to describe the behavior of the HR-PEA of
  • FIG. 1A is a schematic drawing of the first embodiment of system with an HR-PEA of FIG. 1 A attached to a structure of interest from a perspective view.
  • FIG. 5B is a schematic drawing of the system of FIG. 5 A a front view.
  • FIG. 5C is a schematic drawing of the system of FIG. 5 A a side view.
  • FIG. 5D is a schematic drawing of the structure of interest of FIG. 5 A deforming under a vibrational load.
  • FIG. 6 shows plots comparing performance of the HR-PEA of FIG. 5 with a TMD.
  • FIG. 7 is a flowchart of an exemplary embodiment of a method for mitigating vibration in a system.
  • Exemplary embodiments of the present invention include a Hybrid Rotational PEA (HR- PEA).
  • the HR-PEA hybridizes the advantages of both a linear PEA, referred to as tuned mass damper (TMD), and a nonlinear PEA (referred to as nonlinear energy sink (NES)), without suffering from their drawbacks.
  • TMD tuned mass damper
  • NES nonlinear energy sink
  • the HR-PEA performs oscillations (i.e. not full rotations) and acts like a TMD, while for high energies relative to the size and/or mass of the HR-PEA the HR-PEA performs rotations, and serves like a NES.
  • the level of energy intensity (small energy excitations vs. high energies) is relative to the size and/or mass of the PEA, such that a given energy level may be considered to be high for a small PEA and low for a large PEA. Specific numerical examples are provided below.
  • the HR-PEA Due to its essential nonlinearity (due to the rotations), the HR-PEA has the ability to adopt the frequency of the excitation and to resonate with an attached main system, thereby mitigating the effects of load/vibration upon the main system. Since the HR-PEA passively adapts its behavior to respond to small energy and high energy excitations, the HR-PEA provides a highly efficient energy transfer mechanism.
  • FIG. 1 A shows a first exemplary embodiment of a HR-PEA 100.
  • a housing 110 of the HR-PEA 100 may be made of a rigid material which allows the housing 110 to withstand intense external disturbances.
  • the housing 110 is made from stainless steel, but other suitable materials may be substituted for particular applications.
  • the housing 110 is attached to the main system via interface holes 112 located in its bottom face, for example, by bolts or other fasteners.
  • FIGS. IB and FIG. 2 illustrate the internals of HR-PEA of FIG. 1A.
  • a free-swinging weighted arm 180 includes a pivot portion 185 at a first end and an internal mass (IM) 120 at a second end of the weighted arm 180, connected by a connecting beam 130 having a length L.
  • IM internal mass
  • the parameters of the HR-PEA are tuned according to a PS of interest using computational analysis in which the vibration mitigation effect of the HR-PEA with varying parameters is considered.
  • the analysis may be performed, for example, using various simulation programs and software.
  • the PS and the HR-NES were modeled using MATLAB, and the HR-PEA parameters were chosen using numerical optimization.
  • the pivot portion 185 is mounted on a shaft 170 or axle passing through a bearing 160 that allows smooth rotation of the weighted arm 180 around a shaft axis 150.
  • the friction associated with the rotation of the bearing 160 is the source of energy dissipation of the HR- PEA, which is essential for dissipating the energy from the PS by converting it into heat.
  • the shaft 170 may be, for example, a long bolt, which is fixed and tightened to the housing 110 for example, using a nut 117. Sizes and dimensions are shown in the figure below.
  • R indicates the distance between the shaft axis 150 and a center of gravity of the internal mass 120 in a plane of rotation and/or oscillation of the weighted arm 180 within the housing 110.
  • the geometry of the HR-PEA 100 allows the free- swinging weighted arm 180 to perform small amplitude angular oscillations (oscillatory mode) in the plane of rotation when the main system is exposed to low-moderate energy loading, and as shown by FIG. 3B, intense rotations (rotation mode) for high energies.
  • the intensity of a given energy level is relative to the size of the HR-PEA, i.e. a given energy can be high for small HR- PEA and low for a large on. Numerical examples are provided in the example below.
  • Oscillatory mode leads to affect vibration mitigation for low and moderate energies, while rotational mode provides vibration mitigation for moderate to high energies.
  • the process of energy absorption works as follows; undesired vibrational energy enters the PS and makes it vibrate in a corresponding intensity.
  • the PEA which is attached to the PS starts to vibrate as well, due to energy flow from the PS to the PEA in a dynamical mechanism called targeted energy transfer.
  • targeted energy transfer When the energy enters the PEA is dissipated to heat due to the friction of the PEA and in this way leaves the system.
  • the ability of a PEA to absorb and dissipate undesired energy is referred to as its efficiency.
  • the TMS are effective only for narrow frequency and for low energy levels (or intensities) while NES are effective for a broader frequency range and only moderate energy levels.
  • it should be attached to the PS so its orientation will be alleged with the direction of vibration of the PS, because in this way the PEA can absorb the largest amount of energy from the PS.
  • the PS and the HR-PEA (collectively referred to as the overall system 400), are modelled be an equivalent and simplified mechanical system shown in FIG. 4. Even though simplified, this reduced order model 400 captures and describes the relevant dynamical regimes that take place in the overall system.
  • the PS 405 is modelled by the gray square mass with mass M and the PEA with a marble 420 of mass m that can move freely on the circular blue trajectory with arm in length r 0.
  • the direction of oscillation of the PS 405 is denoted by x, and the direction of gravity force by the vector g.
  • the stiffness of the PS 405 is denoted by C and the damping associated with rotations around the shaft is denoted by v.
  • the angle of rotation of the HR-PEA is denoted by Q.
  • u is the displacement of the PS 405 normalized by the arm length of the PEA 420.
  • the dimensionless time scale is denoted by t.
  • the energy captures in the overall system, in the PS 405 and in the FIR-PEA are as follows:
  • the percentile portion of the overall energy that carried by the PEA is denoted by k and given by the following expression:
  • the aim is to find optimal set of design parameters that will allow optimal absorption performances, i.e. will lead to highest values of K.
  • K the amount of energy left in the overall system. For a system which is subjected to impulsive loading, this amount can be described by the following expression:
  • FIGS. 5A-5C For non-limiting exemplary purposes only, a specific example applying the above model to the embodiment of the FIR-PEA 100 of FIG. 1 A is presented.
  • the absorption performances of the HR-PEA 100 are demonstrated by attaching the exemplary HR-PEA 100 to a PS 500, here a multi-story structure 500, as shown by FIGS. 5A-5C.
  • the height H of the exemplary PS 500 is 2000 mm
  • the width W is 750 mm
  • the depth D is 400 mm.
  • the thickness of each story is 10 mm
  • the thickness of the external vertical beams is 20 mm.
  • the structure contains three stories with identical heights.
  • the mass of the PS 500 is 113.5 kg, and the natural frequency of the PS 500 that corresponds to the undesired oscillatory mode is 6.63 Hz.
  • the HR-PEA 100 is mounted to the highest story of the PS 500, where motion of the PS 500 as a result of an applied vibration 505 is of the largest amplitude, i.e. highest vibration energy, as indicated by the thick black arrow shown in FIG. 5B.
  • a plane of oscillation and/or rotation of the weighted arm 180 (FIG. 2) of the HR-PEA 100 is parallel to the applied vibration 505.
  • the mass of the rotating element of the HR-PEA 100 was chosen to be 11.3 kg, here corresponding to approximately 10% of the mass of the PS 500.
  • the HR-PEA 100 may be scaled and adapted to mitigate vibration on systems both larger and smaller than the above example, even much larger and much smaller.
  • FIG. 5D shows a snapshot in time of the PS 500 in a deformed state under an active vibration mode for mitigation, here a first ending mode with a frequency of 6.64 Hz.
  • FIG. 7 is a flowchart of an exemplary embodiment of a method for mitigating vibration in a system.
  • An axle 170 is attached to a housing 110 for a hybrid rotational passive energy absorber 100, as shown by block 710.
  • a free swinging weighted arm 180 is provided with a beam 130 having a length L, a pivot portion 185 disposed at a first end of the beam, and an internal mass 120 at a second end of the beam 130, as shown by block 720.
  • the pivot portion is attached to a bearing (160) on the axle 170 to rotatably connect the pivot portion 185 to the axle 170, as shown by block 730.
  • the bearing is configured to provide smooth motion of the weighted arm around an axis (150) of the axle in a rotation and/or oscillation plane orthogonal to the axis.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

La présente invention concerne un absorbeur d'énergie passive rotatif hybride (100) qui est conçu pour atténuer les effets d'une charge sur un système fixé. Un essieu (170) est ancré à un boîtier (110) au niveau d'une première extrémité d'essieu et d'une seconde extrémité d'essieu. Un bras lesté à oscillation libre (180) comprend une poutre (130) ayant une longueur L, une partie pivot (185) disposée au niveau d'une première extrémité de la poutre et une masse interne (120) au niveau d'une seconde extrémité de la poutre. Un palier (160) relie en rotation la partie pivot à l'essieu. Le palier est conçu pour fournir un mouvement fluide du bras lesté autour d'un axe (150) de l'essieu dans un plan de rotation et/ou d'oscillation orthogonal à l'axe.
PCT/US2020/043603 2020-07-24 2020-07-24 Absorbeur d'énergie passive rotatif hybride WO2022019923A1 (fr)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100107807A1 (en) * 2006-12-15 2010-05-06 Soletanche Freyssinet Device for vibration control of a structure
US20120304808A1 (en) * 2010-02-18 2012-12-06 Toyota Jidosha Kabushiki Kaisha Dynamic damper
US20130326969A1 (en) * 2011-03-04 2013-12-12 Moog Inc. Structural damping system and method
US20160264236A1 (en) * 2015-03-13 2016-09-15 Airbus Helicopters Antivibration suspension system for a tie bar of an aircraft power transmission gearbox, an antivibration suspension system, and an aircraft

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100107807A1 (en) * 2006-12-15 2010-05-06 Soletanche Freyssinet Device for vibration control of a structure
US20120304808A1 (en) * 2010-02-18 2012-12-06 Toyota Jidosha Kabushiki Kaisha Dynamic damper
US20130326969A1 (en) * 2011-03-04 2013-12-12 Moog Inc. Structural damping system and method
US20160264236A1 (en) * 2015-03-13 2016-09-15 Airbus Helicopters Antivibration suspension system for a tie bar of an aircraft power transmission gearbox, an antivibration suspension system, and an aircraft

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
ANONYMOUS: "Tuned Mass Damper Demonstration", INSTRUCTABLES WORKSHOP, 17 February 2016 (2016-02-17), XP055901146, Retrieved from the Internet <URL:https://www.instructables.com/Tuned-Mass-Damper-Demonstration/> [retrieved on 20220315] *

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