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AssigneeTechnical Manufacturing Corporation
InventorWillis J. Reid, III
Estimating the term…
A pneumatic piston assembly wherein a first apertured piston having a piston well is secured by a diaphragm to a pneumatic chamber. A load-supporting element is received in and pivotally engages the floor of the piston well. The load to be isolated directly engages the load-supporting element. Vibrational forces acting on the chamber are primarily absorbed by the piston in a gimbal-like fashion, thereby effectively isolating the supported load from such forces.
In an air isolation system wherein a horizontal surface is isolated from vibrational forces by being supported by pneumatic piston assemblies which assemblies each have a loading chamber and a damping chamber, the chambers being pressurized, the improvement of the pneumatic piston assembly comprising:
In an air isolation system wherein a horizontal surface is isolated from vibrational forces by being supported by pneumatic piston assemblies, which assemblies each have a loading chamber and a damping chamber, the chambers being pressurized and the improvement of the pneumatic piston assembly comprising:
Dependencies are inferred from the claim text.
Details of movements not otherwise provided for: suspensions
Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not…
Housing or supporting of instruments or other apparatus: supports; Devices for carrying
Constructional details of instruments, or comparable details of other apparatus, not otherwise
Term ended 19 Feb 2000 (estimated)
USPTO file history isn’t available for this patent, so only indexed dates are shown.
This invention relates to a vibration isolation system.
Specifically, the invention is directed to a pneumatic vibration isolation device of the "air spring" type which attenuates the horizontal components of disturbing vibrations, while improving the vertical isolation properties of the pneumatic device.
All buildings vibrate and vibrations transmitted through the floor affect instruments and apparatus to varying degrees. A vibration isolation system must have a natural frequency (resonate) materially below the lowest floor frequency. High frequency (over 25 Hz) vibrations can easily be attenuated with traditional static control systems such as a marble slab supported on rubber pads, cork, fiberglass, or inflated bags. Serious problems usually occur when floors vibrate at low frequencies (7-25 Hz). Most static systems resonate in or above this frequency range and therefore, actually amplify low frequency vibrations. Traditional static systems designed for low frequency vibration problems are usually too massive or too unstable to be practical for most applications. Any static low frequency system is very sensitive to load variations which cause level changes in the top surface and obvious operator problems.
FIG. 1 is a perspective view of a vibration-free air isolated table embodying the invention;
FIG. 2 is a front sectional view of an assembly of the preferred embodiment; and,
FIG. 3 is a front sectional view of an alternative embodiment of the invention.
In FIG. 1, a vibration-free isolation table 10 is shown which comprises legs 12, an air isolation system 14 and a top surface 16 illustrated perspectively.
The system 14 includes three valve adjustment pads 18, servo-valves 20, a table air gauge 22, an air inlet 24 and four load carrying pneumatic piston assemblies 30. One piston assembly 30 is shown in detail in FIG. 2.
Referring to FIG. 2, the assembly 30 comprises a load carrying chamber 32, having a floor 34, four walls 36 and an inwardly extending annular plate 38 which is rigidly secured to the table. A fitting 40 connects to a pressure line (not shown) for the introduction of pressurized air into the chamber. A fitting 42 connects to a pressure hose having a orifice which communicates with a pressurized damping chamber (not shown).