WO1997011288A1 - Dispositif antivibratile a amortisseur dynamique - Google Patents

Dispositif antivibratile a amortisseur dynamique Download PDF

Info

Publication number
WO1997011288A1
WO1997011288A1 PCT/GB1996/002332 GB9602332W WO9711288A1 WO 1997011288 A1 WO1997011288 A1 WO 1997011288A1 GB 9602332 W GB9602332 W GB 9602332W WO 9711288 A1 WO9711288 A1 WO 9711288A1
Authority
WO
WIPO (PCT)
Prior art keywords
neutraliser
isolator
vibration isolation
mass
isolation device
Prior art date
Application number
PCT/GB1996/002332
Other languages
English (en)
Inventor
Roger Pinnington
Original Assignee
University Of Southampton
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 University Of Southampton filed Critical University Of Southampton
Priority to AU70894/96A priority Critical patent/AU7089496A/en
Publication of WO1997011288A1 publication Critical patent/WO1997011288A1/fr

Links

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
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • F16F7/108—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on plastics springs
    • 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
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
    • F16F1/371—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by inserts or auxiliary extension or exterior elements, e.g. for rigidification
    • 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
    • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
    • F16F7/116—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on metal springs

Definitions

  • This invention relates to a vibration isolation device or arrangement.
  • This vibration can cause damage to the movable object or disturbance to people or machinery in its vicinity.
  • One conventional method of reducing the transmission of vibrational forces between such objects has been by positioning a relatively flexible isolator between them.
  • the isolator would be made of rubber or a metal spring. This solution does not always adequately reduce the transmission of vibrations.
  • a neutraliser sometimes referred to as a dynamic absorber
  • This approach is often used with buildings.
  • the applied force from the neutraliser is proportional to its mass and acceleration.
  • this has a problem in that the ratio of the mass of the neutraliser to the mass of the object must be about 1:10 to be effective and this can result in fatigue failure in the neutraliser itself.
  • the object e.g. a building, must be designed to withstand this mass .
  • a vibration isolation device for reducing the transmission of vibrations between two objects, the device comprising an isolator providing a load path coupling the objects together, and a neutraliser comprising a neutraliser mass mo ed to a flexible portion, wherein at least a part of the flexible portion of the neutraliser which is distal from the neutraliser mass is incorporated into the load path of the isolator .
  • the device operates more efficiently than conventional devices because the force from the neutraliser is coupled into the load path of the isolator.
  • the force required to drive the velocity at the coupling point to zero is much smaller when applied to the isolator, than when applied to the relatively massive machine.
  • the isolator includes a flexible portion into which the flexible portion of the neutraliser is coupled.
  • the present invention proposes combining the features of both the isolator and the neutraliser such that the force transmitted between the object and the base is reduced.
  • a dip in transfer dynamic stiffness at the natural frequency of the neutraliser occurs when the neutraliser is combined with the isolator. This dip is greatest when the mass of the neutraliser is large relative to the object, but satisfactory results are achieved when the mass of the neutraliser is less than 1/lOth of the mass of the object.
  • the response of the device can be further improved by adjusting the damping of the isolator and/or neutraliser.
  • the neutraliser is configured to act in two perpendicular directions. This may be simply achieved by a symmetric configuration of the neutraliser.
  • the neutraliser mass may be disposed internally of a support in the isolator or of an isolator mass in a plural stage isolator.
  • Examples of types of neutraliser which could be used in the present invention are a double cantilever beam, a bolt embedded in an elastic material or a tensioned wire.
  • a vibration isolation arrangement for reducing the transmission of vibrations between two interconnected objects, the arrangement having a mechanical equivalent circuit constituted by the masses of the two objects interconnected by the series coupling of a first and a second damped elastic compliance and a mass coupled via a third damped elastic compliance to the coupling point of said first and second damped elastic compliancies.
  • Figure 1 illustrates an example of a conventional vibration neutraliser
  • Figure 2 illustrates the variation in force transmissibility with normalised frequency for a mass system having a simple isolator
  • Figure 3 illustrates the variation in force transmissibility with normalised frequency for the system and the neutraliser of Figure 1;
  • Figure 4 shows a measured variation of transfer dynamic stiffness with frequency of a conventional isolator;
  • Figure 5 illustrates a conventional two-stage isolator;
  • Figure 6 illustrates an example of a vibration compensation device in accordance with the present inven ion;
  • Figure 7 shows how the transfer dynamic stiffness of the device of Figure 6 varies with frequency;
  • Figure 8 illustrates a vibration compensation device in accordance with the present invention using a two-stage isolator
  • Figure 9A&9B show how the transfer impedance and the dynamic stiffness vary with frequency for the devices of Figure 5 and Figure 8
  • Figure 10 illustrates an example of the device of Figure
  • Figure 11 illustrates an example of the device of Figure 8 using a cantilever type neutraliser
  • Figure 12 illustrates an example of the device of Figure
  • Figure 13 illustrates an example of the device of Figure
  • Figure 14 shows a two stage isolator wherein the neutraliser is disposed within the isolator mass.
  • FIG. 1 schematically illustrates a conventional vibration neutraliser 1 of mass Ma attached to an object, namely machine 2 of mass M.
  • FIG. 3 shows graphically the variation in force transmissibility with frequency (normalised by the natural frequency of the neutraliser, wa) for different stiffness ratios (neutraliser stiffness/isolator stiffness) .
  • the isolator and neutraliser damping is kept constant at 0.05 and the neutraliser natural frequency, wa is tuned to the natural frequency of the machine-mass system wn.
  • a minimum response is achieved at the neutraliser natural frequency. From Figure 3 it can be seen that increasing the neutraliser stiffness implies an increase in the neutraliser mass.
  • FIG 5 schematically illustrates a conventional two-stage vibration isolator.
  • the machine 2, of mass M is coupled to the foundation 4 by an isolator 3.
  • the two stage isolator comprises two flexible elements, springs 10,11, which are connected via a 2 stg mass 5, Mi.
  • the two stage isolator is often not used because of the resonance peak which occurs at the natural frequency of the system. This peak is shown in Figure 9A by curve 13 and in Figure 9B by the solid curve.
  • FIG. 6 is a schematic diagram of an example of a vibration isolation device in accordance with the present invention.
  • One object, namely machine 2 is coupled to another object, namely foundation (or base) 4 via an isolator 3 (which is one stage) .
  • a vibration neutraliser 6 consisting of a mass 7, Ma coupled via a spring 8 to a support 9 is positioned in the isolator 3.
  • the neutraliser 6 is coupled into the isolator 3 approximately mid-way between its ends, but it could be coupled closer to one end or the other.
  • Figure 7 shows how, for the device of Figure 6, the transfer dynamic stiffness of an example of a vibration compensation device varies with normalised frequency for different stiffness ratios.
  • the isolator and neutraliser damping are constant at 0.3 and 0.05 respectively, while the stiffness ratio is varied.
  • a dip can be seen at the natural frequency of the neutraliser. This is preceded by a maximum.
  • This phenomenom is independent of the natural frequency of the main object-isolator system.
  • the stiffness ratio decreases the preceding peak approaches closer to the dip and so the useful attenuation bandwidth is less. Hence a high ratio is desirable.
  • As with a conventional neutraliser it is best to have as large a neutraliser as possible but the system will operate effectively with much smaller neutralisers than the conventional systems.
  • Figure 8 shows a vibration compensation device in accordance with the present invention and incorporating a two stage isolator.
  • the mass 2 is coupled to the foundation 4 via a vibration isolator 3.
  • the flexible portion of isolator 3 consists of two separate flexible elements, springs 15,16, each coupled to an intermediate mass 14 (sometimes called a blocking mass) .
  • the two stage mass 14 is mounted on the neutraliser support 9.
  • the neutraliser mass 7 is coupled via spring 8 to the support 9.
  • the flexible portion could include a series connection of further flexible elements separated by masses to make it plural-stage.
  • curve 12 shows the variation of transfer impedance with frequency of the device of Figure 8.
  • the use of a two stage isolator and neutraliser in the device of the present invention produces a dip at the natural frequency and improved transfer impedance at other frequencies.
  • the natural frequency of the neutraliser is tuned to coincide with the natural frequency of the two stage system resulting in a reduced resonance peak at the expense of introducing two new peaks either side of the original. On average however the response is less than the original .
  • Figure 9B shows the effect of changing the neutraliser properties to obtain some optimization.
  • the two dotted lines in Figure 9B show, for two different configurations of the device of Figure 8, the variation of dynamic transfer stiffness with frequency, as compared to the conventional two stage mount shown by a continuous line.
  • the stiffness ratio ka/2k 0.4
  • the natural frequency ratio f a /f I 0.5
  • the shape of the curve can be altered by tuning the neutraliser as compared to the isolator-object system.
  • the neutraliser is a mass coupled to a flexible portion which is a rubber mix
  • the properties may be selected by altering constitution of the rubber mix and the size of the mass.
  • Figure 10 shows a double cantilever beam 19 coupled into isolator 23 made of rubber and acting as a spring with masses 17, 18 connected to each end.
  • the system is driven by an electrodynamic shaker 36 including magnet 37 and coil 38 coupled to one end of the isolator.
  • An accelerometer and a force transducer 39 measure the displacement and force produced by the shaker 36 at that one end.
  • a further force transducer 40 measures the transmitted force, at the other end.
  • the cantilever beam acts as the neutraliser, the stiffness and natural frequency of which can be estimated using simple theory:
  • the effective length of the beam 19 was taken as the distance from the centre line 20 of the isolator 23 to the centre line 21 of the mass 17. Errors in this calculation arise from the fact that the boundary conditions at the supported end of the beam are not ideally clamped and the effect of the mass of the beam 19 is not properly considered. The latter effect is assumed to be negligible as the mass of the cantilever beam 19 is small compared to the added masses 17, 18. Note the above formula is for a single cantilever. For the double cantilever beam used in the experiment, the total stiffness of the neutraliser can be considered as twice that of a single beam.
  • the stiffness ratio was varied by changing the neutraliser mass and adjusting it along the length of the beam so that the natural frequency stayed the same. As a comparison, if neutraliser 19 was positioned at the top of the isolator 23 it would act as a conventional neutraliser.
  • a variation on this configuration is to use two double cantilever beams (not shown) with different natural frequencies.
  • Two modes are advantageous.
  • the first mode is with the natural frequency of the second beam equal to twice that of the first. This could.be useful to reduce the force transmitted from a machine at both 1 x and 2 x RPM of the machine.
  • the second mode is with the natural frequency of the second tuned to coincide with the response peak of the first to improve the response achieved.
  • a mass 24 of steel was positioned between two pieces of rubber 25, 26 to create a two stage isolator.
  • the cantilever 19 was positioned in the mass 24 to act as a neutraliser.
  • the neutraliser is tuned so that its natural frequency coincides with the natural frequency of the two stage isolator.
  • a small diameter steel bolt 27 is embedded in a thick rubber plate 28 which is the isolator by drilling a hole through the rubber and press fitting the bolt 27 through the hole.
  • the stiffness of the rubber acting on the bolt acts as the neutraliser stiffness.
  • the neutraliser mass and so natural frequency can be varied by adding masses 29 to the bolt.
  • a wire 30 is connected to a plate 31 at the centre of the isolator 33. Masses 32, 34 are connected to the wire 30 which is tensioned on a rigid frame 35. At its natural frequency the wire-mass system acts as a vibration neutraliser. The natural frequency can be varied by changing the wire tension using a threaded screw (not shown) .
  • Figure 14 shows, in cross section, a two stage isolator which is particularly suitable as an engine mount.
  • the neutraliser is disposed inside the isolator mass which provides a compact structure.
  • a mass 45 is connected between two flexible elements 43,44 each being a pair of legs made of rubber and being connected to a respective flange 41,42.
  • the flanges 41,42 are for mounting the isolator to respective objects.
  • the isolator mass 45 is a cylinder with a cylindrical hollow, and disposed therewithin is the neutraliser 46 consisting of a neutraliser mass 47 embedded in an elastomeric material 48 such as rubber.
  • the circular symmetry visible in the cross section allows the neutraliser 46 to act on vibrations polarised in directions parallel and perpendicular to the flanges 41, 42.
  • the isolator mass 45 and neutraliser mass 47 may be spherical, whereby the neutraliser acts on vibrations polarised in all directions parallel to the flanges 41, 42, in addition to vibrations polarised perpendicular to the flanges 41,42.
  • Possible uses of the present invention are for an isolator tuned to the natural frequency of a building which is vulnerable to earthquake, or to suppress the natural frequency of a two-stage mount, so that it can be used under an automobile engine.
  • a stiff mount could be used to provide a good quality ride while a double mount could be used to attenuate high frequency vibrations.
  • Other transport uses are in ships and trains.
  • Another application is removal of troublesome excitation frequencies, for example, the spinning of electrical machines or spin dryers where a stiff isolator could be used with a neutraliser within it tuned to the excitation frequency.

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

Abstract

Cette invention concerne un dispositif antivibratile qui comporte un isolateur(3) permettant de coupler un objet (2) et une base (4) ainsi qu'un organe de neutralisation (6) couplé à l'isolateur par insertion à l'intérieur de ce dernier. Lorsqu'une baisse de la raideur dynamique de transfert se produit à la fréquence naturelle de l'organe de neutralisation (6), il est possible de syntoniser ladite raideur dynamique à une fréquence caractéristique de l'objet (2) ou à une fréquence naturelle de l'ensemble objet-isolateur (3, 6), en particulier lorsque ledit isolateur (3) est un isolateur à deux étages. L'organe de neutralisation (46) peut être une masse sphérique (47) noyée dans du caoutchouc (48) à l'intérieur d'une masse isolante creuse (45) elle-même reliée à deux éléments isolants (43, 44).
PCT/GB1996/002332 1995-09-19 1996-09-18 Dispositif antivibratile a amortisseur dynamique WO1997011288A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU70894/96A AU7089496A (en) 1995-09-19 1996-09-18 Vibration isolation device with a dynamic damper

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB9519118.5A GB9519118D0 (en) 1995-09-19 1995-09-19 Vibration compensation device
GB9519118.5 1995-09-19

Publications (1)

Publication Number Publication Date
WO1997011288A1 true WO1997011288A1 (fr) 1997-03-27

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1996/002332 WO1997011288A1 (fr) 1995-09-19 1996-09-18 Dispositif antivibratile a amortisseur dynamique

Country Status (3)

Country Link
AU (1) AU7089496A (fr)
GB (1) GB9519118D0 (fr)
WO (1) WO1997011288A1 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001051295A1 (fr) * 2000-01-14 2001-07-19 Rexam Ab Dispositif de mise en forme et de marquage de cible
US6455806B1 (en) 2000-01-14 2002-09-24 Rexam Ab Arrangement for shaping and marking a target
US6476349B1 (en) 1998-04-28 2002-11-05 Rexam Ab Strip guiding device
US6479787B1 (en) 1999-10-05 2002-11-12 Rexam Ab Laser unit and method for engraving articles to be included in cans
US6576871B1 (en) 2000-04-03 2003-06-10 Rexam Ab Method and device for dust protection in a laser processing apparatus
US6872913B1 (en) 2000-01-14 2005-03-29 Rexam Ab Marking of articles to be included in cans
US6926456B1 (en) 2000-01-20 2005-08-09 Rexam Ab Guiding device for a marking arrangement
EP1657362A1 (fr) 2003-07-11 2006-05-17 Pandrol Limited Amortisseurs accordés pour rail de chemin de fer
EP1752683A1 (fr) * 2004-04-21 2007-02-14 Kabushiki Kaisha Kobe Seiko sho Structure de reduction des vibrations et de raccord
NL2014378B1 (nl) * 2015-03-02 2016-10-14 Loggers B V Inrichting met gedempte dekopbouw.
CN110332271A (zh) * 2019-08-06 2019-10-15 宜达工程设计（天津）有限责任公司 一种嵌套式减震器
WO2024037584A1 (fr) * 2022-08-17 2024-02-22 广东美的白色家电技术创新中心有限公司 Structure de transfert de force, ensemble d'emballage, ensemble appareil électrique, couvercle d'écran de filtre et appareil électrique

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2807160A1 (de) * 1978-02-20 1979-08-30 Continental Gummi Werke Ag Lagerelement zum elastischen unterstuetzen insbesondere von motoren in kraftfahrzeugen
US4403762A (en) * 1981-02-20 1983-09-13 General Motors Corporation Low force transmissibility mount
US4420134A (en) * 1980-10-27 1983-12-13 Kaman Aerospace Corporation Vibration isolator with crank driven inertia bar
SU1087718A1 (ru) * 1983-01-25 1984-04-23 Институт Машиноведения Им.А.А.Благонравова Виброизолирующа опора
JPS61105320A (ja) * 1984-10-29 1986-05-23 Mitsubishi Heavy Ind Ltd 防振ゴム
EP0428949A1 (fr) * 1989-11-20 1991-05-29 Psa Sistemi Antivibranti S.P.A. Support pour moteur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2807160A1 (de) * 1978-02-20 1979-08-30 Continental Gummi Werke Ag Lagerelement zum elastischen unterstuetzen insbesondere von motoren in kraftfahrzeugen
US4420134A (en) * 1980-10-27 1983-12-13 Kaman Aerospace Corporation Vibration isolator with crank driven inertia bar
US4403762A (en) * 1981-02-20 1983-09-13 General Motors Corporation Low force transmissibility mount
SU1087718A1 (ru) * 1983-01-25 1984-04-23 Институт Машиноведения Им.А.А.Благонравова Виброизолирующа опора
JPS61105320A (ja) * 1984-10-29 1986-05-23 Mitsubishi Heavy Ind Ltd 防振ゴム
EP0428949A1 (fr) * 1989-11-20 1991-05-29 Psa Sistemi Antivibranti S.P.A. Support pour moteur

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 010, no. 291 (M - 522) 3 October 1986 (1986-10-03) *

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6476349B1 (en) 1998-04-28 2002-11-05 Rexam Ab Strip guiding device
US6479787B1 (en) 1999-10-05 2002-11-12 Rexam Ab Laser unit and method for engraving articles to be included in cans
US6872913B1 (en) 2000-01-14 2005-03-29 Rexam Ab Marking of articles to be included in cans
US6455806B1 (en) 2000-01-14 2002-09-24 Rexam Ab Arrangement for shaping and marking a target
EP1123815A1 (fr) * 2000-01-14 2001-08-16 Rexam Beverage Packaging AB Système pour former et marquer un objet
WO2001051295A1 (fr) * 2000-01-14 2001-07-19 Rexam Ab Dispositif de mise en forme et de marquage de cible
US6926456B1 (en) 2000-01-20 2005-08-09 Rexam Ab Guiding device for a marking arrangement
US6576871B1 (en) 2000-04-03 2003-06-10 Rexam Ab Method and device for dust protection in a laser processing apparatus
EP1657362A1 (fr) 2003-07-11 2006-05-17 Pandrol Limited Amortisseurs accordés pour rail de chemin de fer
EP1752683A1 (fr) * 2004-04-21 2007-02-14 Kabushiki Kaisha Kobe Seiko sho Structure de reduction des vibrations et de raccord
EP1752683A4 (fr) * 2004-04-21 2009-05-20 Kobe Steel Ltd Structure de reduction des vibrations et de raccord
NL2014378B1 (nl) * 2015-03-02 2016-10-14 Loggers B V Inrichting met gedempte dekopbouw.
CN110332271A (zh) * 2019-08-06 2019-10-15 宜达工程设计（天津）有限责任公司 一种嵌套式减震器
WO2024037584A1 (fr) * 2022-08-17 2024-02-22 广东美的白色家电技术创新中心有限公司 Structure de transfert de force, ensemble d'emballage, ensemble appareil électrique, couvercle d'écran de filtre et appareil électrique

Also Published As

Publication number Publication date
GB9519118D0 (en) 1995-11-22
AU7089496A (en) 1997-04-09

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