Abstract
The article discusses the design and also presents a mathematical model and method for calculation of static characteristics of a hydrostatic thrust bearing with a membrane-type displacement compensator. Formulae for calculation of compliance and load characteristics of the bearing are also presented, as well as deformation and compliance of the membrane at which zero compliance of the bearing is guaranteed.
Highlights
Units with non-contact hydrostatic slide bearings are widely used in metal-cutting machines for precision and high-speed machining, micro-machining, in heavy and unique machine tools
The main prospects for further research and development in this area of science and technology are in the area of creation and complex use of spindle assemblies and guides with adaptive hydrostatic bearings, which have regulators of active lubricant injection, in metal-cutting machines
In comparison with bearings with active flow rate compensation, such structures are distinguished by significantly lower energy consumption and the ability to compensate for movements with amplitudesat which other hydrostatic bearings would be obviously inoperative [6]
Summary
Units with non-contact hydrostatic slide bearings are widely used in metal-cutting machines for precision and high-speed machining, micro-machining, in heavy and unique machine tools. The main prospects for further research and development in this area of science and technology are in the area of creation and complex use of spindle assemblies and guides with adaptive hydrostatic bearings, which have regulators of active lubricant injection, in metal-cutting machines. Mechanical engineering, and heavy machine-tool construction, needs such hydrostatic bearings with active displacement compensators that have the ability to provide low positive, as well as zero and negative compliance [6, 7]. By varying the compliance coefficient km of the membrane 3, in particular its thickness, it is possible to achieve the required value of its deformation hm so that the total displacement hs = hm + h of the suspended Disk 4 relative to Disk 1 will have a lower compliance in comparison with the usual bearing k = −∂hs / ∂f , inclu– ding zero and negative compliance
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