WO2007095759A1 - Dispositif de rangement d'equipement audio - Google Patents

Dispositif de rangement d'equipement audio Download PDF

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Publication number
WO2007095759A1
WO2007095759A1 PCT/CA2007/000301 CA2007000301W WO2007095759A1 WO 2007095759 A1 WO2007095759 A1 WO 2007095759A1 CA 2007000301 W CA2007000301 W CA 2007000301W WO 2007095759 A1 WO2007095759 A1 WO 2007095759A1
Authority
WO
WIPO (PCT)
Prior art keywords
shelf
support
vibration
support structure
grooves
Prior art date
Application number
PCT/CA2007/000301
Other languages
English (en)
Inventor
John Wiebe
Original Assignee
Sonic Integrity Canada Ltd.
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 Sonic Integrity Canada Ltd. filed Critical Sonic Integrity Canada Ltd.
Publication of WO2007095759A1 publication Critical patent/WO2007095759A1/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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47B—TABLES; DESKS; OFFICE FURNITURE; CABINETS; DRAWERS; GENERAL DETAILS OF FURNITURE
    • A47B81/00—Cabinets or racks specially adapted for other particular purposes, e.g. for storing guns or skis
    • A47B81/06—Furniture aspects of radio, television, gramophone, or record cabinets

Definitions

  • the present invention relates generally to the field of vibration isolation mechanisms in a shelving unit or cabinet, and, more particularly, to vibration control devices which provide improved inherent vibration control in a shelving unit or cabinet in an economical fashion.
  • the shelving unit or cabinet is well suited for use with, for example, audio equipment or other vibration sensitive equipment.
  • vibration particularly that which is referred to as "micro" vibration within the audio equipment, such as with compact disk (“CD”) players, preamplifiers, amplifiers, phonograph stages, and turntables.
  • a primary source of vibration in audio equipment is caused by the sound waves generated by the audio equipment, particularly if the equipment is operated at louder volumes, or repeatedly generates audio frequencies at selected harmonic frequencies.
  • Other, "macro" vibrations may also happen when a door is slammed, the equipment is bumped, or even from floor movement caused by a person walking in the room.
  • vibration isolation devices such as mounting feet
  • Vibration absorbing materials are limited in the capability to attenuate vibration.
  • Spikes and cones "drain" vibration to the ground or other support surface, rather than actually isolating the performance device from the vibration; and sand boxes, by definition, include the use of sand, which can be very messy and necessarily creates the risk of inadvertent introduction of sand particles and dust into expensive performance equipment, accessories, tapes, compact disks, and anything else in the vicinity of use of the sand.
  • US Patent No. 6550879 does provide a cabinet structure which attempts to address this issue, but merely relies on a series of strengthening pieces to be added to a traditional cabinet. These strengthening materials preferably have a honeycomb structure in order to dampen the vibration from the sound waves. As such, it would be desirable to provide additional means to isolate the vibration sensitive equipment from extraneous vibrations, and preferably accomplish this isolation by features inherently present in the shelving unit or cabinet on or in which, the equipment rests.
  • the present invention was developed with the goals of providing a vibration isolating device which inherently provided in the cabinet or support shelf on which the vibration equipment rests, so as reduce, ameliorate, or eliminate the deleterious effects caused by vibration in vibration sensitive equipment. It is further among the advantages of the present invention that the new vibration reduction devices be suitable for manufacture in a variety of sizes or models so as to be capable of handling various sizes of loads and a variety of applications.
  • the vibration control devices be an inherent feature of the cabinet or a support shelf which are used to house or support the vibration sensitive equipment.
  • the present invention provides a vibration control support structure for use with vibration sensitive equipment, wherein said support structure comprises a shelf and a shelf support device and either or both of said shelf and said shelf support device comprise a vibration attenuating structure.
  • the shelf and shelf support device can be free standing, or alternatively, can be part of a complete cabinet structure.
  • the present invention also provides a support shelf for use in the vibration support structure, wherein said support shelf comprises a vibration attenuating structure.
  • the shelf of the present invention is provided with at least one surface feature which attenuates the vibration resonant in the shelf structure.
  • Preferred surface features include providing a zone of a vibration absorbing structure or materials, and in a most preferred embodiment, the surface feature is provided by a plurality of grooves or ridges which have preferably been created on at least a portion of one side of said shelf. In a preferred structure, the surface feature is provided by a series of regularly spaced, parallel grooves which have been cut or milled into the lower surface of the shelf.
  • the present invention also provides shelf support device for use in the vibration support structure, wherein said shelf support device comprises a vibration attenuating structure.
  • the shelf support device of the present invention is provided with at least one surface or composition feature which attenuates the vibration which is ultimately resonant in the shelf structure.
  • prior art shelf support devices are made of a materials such as wood, or tubular aluminum, tubular steel or the like, which can aid in the transmission of any vibration to the shelf.
  • the shelf support device of the present invention is preferably made of a vibration absorbing material or a vibration dispersive material.
  • a preferred vibration absorbing material is a composite fiber material, and most preferably, a hollow tube which has been fabricated from a carbon fibre material.
  • a vibration dispersive material is a solid metallic rod, and most preferably, a solid aluminium rod, which acts to cause increased radial dispersion of the vibration within the support and thus, less propagation of the vibration along the support.
  • the shelf support device can be a single support or a plurality of support devices, such as, for example, a plurality of carbon fibre tubes or a plurality of solid aluminium rods.
  • the vibration control device of the present invention provides a method and apparatus for attenuating the vibrations typically encountered on shelf which is used to support vibration sensitive equipment, and/or which is in contact with such equipment.
  • Figure 1 is a top perspective view of a storage shelf according to the present invention
  • Figure 2 is a bottom view of a shelf used in the present invention
  • Figure 3 is a cross sectional view of a portion of the shelf of Figure 2.
  • vibration sensitive equipment and the like are meant to include sound equipment, as well as video and other sophisticated or scientific equipment which is subject to negative effects of external and internal vibrations.
  • audio or “sound production” equipment will often be used inclusively of any and all types of equipment, the performance of which will benefit from support of the equipment on the new noise reduction devices described below.
  • the new vibration control device of the present invention will sometimes hereafter be referred to simply as the "device”.
  • a vibration control device 10 having 3 support shelves 12, and 4 vertical shelf support devices 14.
  • the support shelves and vertical support devices are used in the construction of racks or stands for stereo and video system components.
  • the primary design of device 10 consists of medium density fibreboard (MDF) shelves 12 supported by circular support sections 14 in the shape of circular rod or tubes. The shelves are stacked one above another and individual electronic components are placed on each shelf.
  • MDF medium density fibreboard
  • shelves 12 are fabricated from any of a variety of materials, including, wood laminates, composite wood materials such as MDF, particle board, chip board, or the like, metal, plastic, or glass panels, composite materials such as carbon fibre materials, or various epoxy, fibreglass or acrylic resin based materials, or stone such as granite, or combinations thereof.
  • wood laminates composite wood materials such as MDF, particle board, chip board, or the like
  • metal, plastic, or glass panels composite materials such as carbon fibre materials, or various epoxy, fibreglass or acrylic resin based materials, or stone such as granite, or combinations thereof.
  • the skilled artisan will readily be able to determine any one of a number of suitable shelf materials.
  • shelves 12 are manufactured from a 16 mm thick sheet of wood veneer MDF (Medium Density Fibreboard).
  • Shelves 12 are shown all having the same overall dimensions, however, in alternative configurations, each of shelves 12 can have different shapes or sizes.
  • shelves 12 have a width of 75 cm wide, a depth of 50 cm deep, and a thickness of 2 cm. In alternative embodiments, shelves 12 can have a wide variety of dimensions, but typically, the shelves are between 50 and 125 cm wide, 45 to 60 cm deep, and 1.25 to 3 cm thick. On their top surfaces 16, shelves 12 are preferably substantially flat.
  • the lower surface 18 of shelves 12 are fabricated so as to have a plurality of channeled grooves 20.
  • These grooves are preferably routered into the underside of the shelf, and can be set at any angle between 1 and 179 degrees, relative to the front surface of the shelf. In Figure 2, the grooves are set at an angle of 45 degrees to the front surface 24 of the shelf.
  • the channeled grooves 20 can vary in depth, but preferably are between 1 mm and 55 mm.
  • the depth of channeled grooves 20 is such that they do not extend through more than 75% of the thickness of shelf 12, and more preferably, through no more than 50% of the thickness of shelf 12.
  • channeled grooves 20 have a depth of 5 mm.
  • All of channeled grooves 20 in the present embodiment have a common width of 8 mm, and all grooves 20 are triangular, or V-shaped, as shown in Figure 3. Other groove shapes, such as semi-circular, square or the like, might also be used.
  • the channeled grooves 20 are also spaced 25.4 mm apart (center to center), although this value can vary depending on the shelf design. Typically, the shelves are spaced between 10 and 50 mm apart, and more preferably, between 15 and 30 cm apart.
  • the channeled grooves 20 preferably extend to cover at least over 50% of the surface area of the lower surface 18 of shelf 12. More preferably, however, the channeled grooves cover an area of over 70% of the shelf lower surface area 18, and even more preferably, cover an area of over 80% of the lower shelf surface area 18.
  • a rim 28 is left around the outer edge area of lower shelf surface
  • the depth, width, number, and spacing design features can all be varied depending on the nature of the shelf design, the shelf construction material or other factors. However, by simple measurement of the shelf vibration during testing, these design parameters can be optimized.
  • Vertical shelf support devices 14 are fabricated from hollow carbon fiber tubes. However, they might also be fabricated from solid metallic rods, and in particular, solid aluminium rods. The ciruclar support devices are particularly useful in the shelf arrangement shown in Figure 1 , but are also suitable for use in any "rack" mounted arrangements or designs.
  • Vertical support devices 14 are manufactured to fit within the spaces 28 in shelves 12, and while support device 14 has a diameter of 2.5 cm, the support device diameter can vary from 1.25cm ID to 7.62cm ID.
  • the height of the vertical support devices 14 can also vary depending on the proposed application, but typically vary from 2.5 cm to 46 cm depending of the shelf design of the rack or platform.
  • the improvement in sound of electronic components supported on shelves 12 with carbon fiber vertical supports 14 is a result of the carbon fiber dissipating the vibrations traveling through the upright supports. It is believed that the carbon fiber resonates at such a low frequency that there is very little stimulation within the uprights. This result in a more stable support for the shelves.
  • Carbon fiber can refer to carbon filament thread, or to felt or woven cloth made from those carbon filaments. By extension, it is also used informally to mean any composite material made with carbon filament, such as for example, graphite-reinforced plastic.
  • a typical carbon fiber support comprises carbon filaments, wherein each carbon filament is made out of long, thin sheets of carbon similar to graphite.
  • a common method of making carbon filaments is the oxidation and thermal pyrolysis of polyacrylonitrile (PAN), a polymer used in the creation of many synthetic materials. Like all polymers, polyacrylonitrile molecules are long chains, which are aligned in the process of drawing fibres. When heated in the correct fashion, these chains bond side-to-side, forming narrow graphene sheets which eventually merge to form a single, jelly roll-shaped filament. The result is usually 93-95% carbon. Lower-quality fiber can be manufactured using pitch or rayon as the precursor instead of PAN. The carbon can become further enhanced, as high modulus, or high strength carbon, by heat treatment processes.
  • Carbon heated in the range of 1500-2000°C exhibits the highest tensile strength (820,000 Psi), while carbon fibre heated from 2500-3000 0 C (graphitizing) exhibits a higher modulus of elasticity (77,000,000 Psi).
  • Carbon fiber thread is rated by the number of filaments per thread, in thousands.
  • 3K (3,000 filament) carbon fiber is 3 times as strong as IK carbon fiber, but is also 3 times as heavy.
  • Carbon fiber is most notably used to reinforce composite materials, particularly the class of materials known as graphite reinforced plastic.
  • the carbon fiber thread is typically woven into a carbon fiber cloth. The appearance of this cloth generally depends on the size of thread and the weave chosen.
  • the carbon fiber cloth, or the like can then be used to prepare a hollow tube or solid rod by blending it with a suitable polymeric material to produce a graphite- reinforced plastic (GRP).
  • GRP graphite- reinforced plastic
  • a filament winder can be used to make pieces.
  • FRP fibre-reinforced plastic
  • FRP is a composite material comprising a polymer matrix reinforced with fibres usually of glass, carbon, or aramid and is commonly used in aerospace, automotive and marine industries.
  • the term FRP is a more general description of materials like GRP.
  • the polymer is usually an epoxy, vinylester or polyester thermosetting plastic.
  • CFRP carbon fiber reinforced plastic
  • CFRP carbon fiber reinforced plastic
  • CFRP carbon fiber reinforced plastic
  • the plastic is most often epoxy, but other plastics, like polyester or vinylester, can also be used.
  • GRP matrix can have a profound effect on the properties of the finished composite.
  • a preferred plastic for this application is graphite epoxy.
  • Improvements in sound quality from music played from components placed on shelf s or platforms supported by carbon fiber supports is substantial when listening tests are conducted. Vibration tests show that there is less resonance when carbon fiber tubes and rods are used for supporting shelf s or platforms, as shown in the attached Examples.
  • a simple shelf for an audio rack could be a simple rectangular plate with a given thickness. This shelf would have parallel faces on top-bottom, front-back, and side-side. Standing waves, resulting from either surrounding sounds or the harmonic operations within an audio component transferred through the feet of the component to the shelf, could bounce back and forth between faces, muddying the sound. This is analogous to the standing waves within a listening room.
  • a vibration/sound source When a vibration/sound source is present at either the floor of a rack or on a shelf, it causes the end of a support column to vibrate. This vibration then travels through the support column to cause an adjacent shelf to vibrate, and distort the sound produced.
  • vibrations can propagate to a much larger degree radially, resulting in a less direct path of travel from shelf to shelf for parts of the vibrations.
  • using a solid rod compared to prior art hollow tubing results in having approximately twice the material in which to absorb the heat from vibrations.
  • Using a solid rod instead of prior art hollow tubing not only create less direct paths of propagation for the vibrations, but the solid rods act as more effective 'heat sinks' to reduce the amount of time a vibration will maintain a sound-affecting amplitude. Since the vibrations produced by bass sound and by 50 Hz or 60 Hz electrical supply 'hum' in audio components have longer wavelengths compared to treble frequencies, fewer cycles are required to cover the distance from one end of a support column to the opposite end.
  • High frequency/small wavelength frequencies are more likely to dissipate between ends of a support column due to the greater number of cycles required to travel the length of the support column no matter whether the support column is solid or hollow.
  • improvements in vibration dissipation of support columns should result in more pronounced improvements in sound quality compared to higher frequencies.
  • the large mass of the solid rod might be the result of better energy dissipation, and the larger mass of the solid rod is able to dissipate the energy more effectively than a tubular metallic support.
  • a carbon fiber tube for example, is better able to absorb the vibration energy than a tubular metallic support since the vibration energy is contained, and then absorbed within the carbon fibre, and preferably the tubular carbon fibre, support.
  • test frequencies chosen were multiples of 60 Hz. As such, the test frequencies used were 60 Hz, 120 Hz, 240 Hz, 600 Hz, 1200 Hz, 3000 Hz, and 6000 Hz.
  • This loudspeaker (System-Audio S2K) consisted of a tweeter and a mid-bass driver. It was supported by a two-piece stabilizing cone/spike on each corner. The location of each cone/spike was consistent for each test rack configuration. As a result, both acoustic vibrations and direct mechanical vibrations from the loudspeaker would be transmitted into the top shelf of the test racks.
  • the voltage of the signal fed to the loudspeaker produced a sound pressure level (SPL) of approximately 96 dB @ 1 m, A- weighted.
  • test racks consisted of two shelves separated by four support columns placed approximately at each corner.
  • the shelves consisted of 5/8 in. (16 mm) MDF,
  • the support columns were circular in cross-section, with a diameter of 25.4 mm (1.00 in.).
  • the distance between the support columns was 354 mm in the depth direction, and 558 mm in the width direction.
  • the basic shape of the shelves was altered slightly for the different test configurations.
  • a small (76.2 mm) 'foot' was fastened to the underside of the bottom shelf directly underneath the support columns.
  • the entire rack was placed on a wooden test bench, and the location of the 'feet' marked to ensure each rack was placed in the same position.
  • the first point was the centre of the shelf (Point A/1).
  • the second test point was the centre between the support columns (Point B/2). This was 26 mm rearward of the first point.
  • the third point (Point C/3) was 7 mm from the side edge of the shelf, in-line with point B.
  • the fourth point was 0.618 of the distance from one side to the other, and 0.618 of the distance from the rear to the front of the shelf (Point D/4).
  • the vibrations generated in the shelves were measured using a scanning laser vibrometer.
  • the velocity amplitude of the vibrations in the shelves were recorded, both with the loudspeaker 'on' and with the loudspeaker 'off. This was done to determine the noise of the system.
  • the data was recorded and saved. The data was then used to generate logarithmic graphs comparing velocity amplitude to frequency.
  • the 'base' shelf was the shelf was a CORE rack product that had radiused corners, bevelled edges, and the routered grooves on the underside.
  • a second shelf consisted of the CORE shelf, but with smaller grooves.
  • a third shelf consisted of the CORE shelf, but without grooves.
  • a fourth shelf consisted of a simple rectangular MDF shelf with the same outer dimensions as the CORE shelf.
  • the base CORE shelf was tested with a solid aluminum rod 228.6 mm long vertical support.
  • the solid aluminium tubing was 228.6 mm long.
  • carbon fibre tubing of 228.6 mm was used.
  • a solid aluminium rod of 205.5 mm length was used.
  • a carbon fibre tube with a length of 213.0 mm was used. This length was based on a multiple of the approximate wavelength of a 60 Hz sound wave at room temperature, multiplied by 1.618.
  • the forced vibration analysis of the various test rack configurations indicates that the greatest effect on subjective sound quality by the support rack is caused by frequencies greater than 60 Hz and less than approximately 1200 Hz.
  • the carbon fibre tubing exhibited lower vibration velocity amplitude between 120 Hz and 600 Hz than for the solid aluminum rod supports.
  • the rectangular shelves exhibited greatly larger vibrations as a result of ambient/external vibrations.
  • Carbon fibre tubing generally had the best dampening of ambient/external vibrations.
  • substantially planar is intended to mean planar, nearly planar and/or exhibiting characteristics associated with a planar element.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

L'invention concerne des modifications apportées à des éléments structuraux de râteliers / d'étagères destinés à des étagères à composants et, en particulier, à des composants audio afin d'améliorer le son produit par le système en minimisant les effets des vibrations sur l'équipement positionné sur les étagères. En particulier, l'ajout d'une série de rainures à la surface inférieure de chaque étagère s'est avéré contribuer à l'atténuation des vibrations mesurées sur la surface de l'étagère. De plus, l'utilisation de supports verticaux fabriqués à partir d'un tube en matériau composite à fibres, comme du plastique renforcé par des fibres de carbone / de graphite (GRP) ou un support métallique plein, comme un support fait d'une barre d'aluminium, s'est également avérée atténuer les vibrations mesurées sur la surface de l'étagère. A ce titre, l'invention concerne un procédé et un dispositif destinés à remédier aux effets des vibrations sur des équipements sensibles aux vibrations.
PCT/CA2007/000301 2006-02-22 2007-02-21 Dispositif de rangement d'equipement audio WO2007095759A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CA 2537481 CA2537481A1 (fr) 2006-02-22 2006-02-22 Dispositif de rangement d'equipement audio
CA2537481 2006-02-22

Publications (1)

Publication Number Publication Date
WO2007095759A1 true WO2007095759A1 (fr) 2007-08-30

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CA (1) CA2537481A1 (fr)
WO (1) WO2007095759A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4493471A (en) * 1983-02-14 1985-01-15 Mcinnis Donald E Sound speaker stand for attenuating vibrations
US5197707A (en) * 1991-07-29 1993-03-30 Kohan Barry A Isolation platform and method
US6056381A (en) * 1993-05-07 2000-05-02 Turner; Gary John Vibration isolation platform
US6098822A (en) * 1999-05-04 2000-08-08 Decade Industries, Inc. Shelving system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4493471A (en) * 1983-02-14 1985-01-15 Mcinnis Donald E Sound speaker stand for attenuating vibrations
US5197707A (en) * 1991-07-29 1993-03-30 Kohan Barry A Isolation platform and method
US6056381A (en) * 1993-05-07 2000-05-02 Turner; Gary John Vibration isolation platform
US6098822A (en) * 1999-05-04 2000-08-08 Decade Industries, Inc. Shelving system

Also Published As

Publication number Publication date
CA2537481A1 (fr) 2007-08-22

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