The high pliability of gas-static bearings limits their applicability in spindles of metal-cutting machines. Two methods of reducing the pliability (sometimes to zero or negative values) are known: 1) the use of input units that compensate the lubricant flow rate [1, 2]; 2) the use of units that compensate the motion of elements separated by a gas layer [3, 4]. Such gas-static bearings, operating at negative pliability, may be used to compensate the positive pliability of elastic elements in the metal-cutting machine, so as to improve machining. We know that bearings with active compensation of the lubricant flow rate are characterized by high energy consumption, unstable static properties, and inability to ensure negative pliability at moderate and high loads [1]. Bearings with active motion compensation are largely free of these problems but are structurally more complex. This is true especially of radial bearings [4]. In the present work, we consider a new method of reducing the pliability, in which lubricant-outflow regulators are employed. The resulting radial gas-static bearings are relatively simple in design (Fig. 1). The bearing consists of housing 1 , shaft 2 (subject to external load f ), and two symmetric (relative to the bearing’s central plane) rigid annular elements 3 , connected hermetically to housing 1 by means of elastic elements (membranes) 4. A double gas-choking system in the pressure lines ensures stability of the bearing [5]. The gas (at pressure p in ) is sent in the pressure line through choking annular slots 6 to intermediate flow cavity 7 at pressure p r ; then to thin lubricant gaps 5 (thickness h r ), formed by housing 1 and elastic membranes 4 ; and to intermediate damping annular slots 8 . Overcoming the resistance of these slots, the gas falls at pressure p f into thin supporting gas layer 9 (thickness h ) and passes from the bearing to the surroundings at pressure p a through a gap of thickness h f . Under the action of load f , shaft 2 shifts its position, and the hydraulic drag at the lubricant layers h , h r , and h f changes. In the loaded section, p r and p f increase; in the unloaded section, they decrease. In reaction, forces act on element 3 and membrane 4 in the region of the gaps h r and h f and they are displaced in the opposite direction to the load, as follows from an analysis of the pressure distribution at the working surfaces of element 3 and membrane 4 . Consequently, there is greater increase in hydraulic drag and hence in gas pressure in the loaded end region of the supporting layer and greater decrease in these factors in the unloaded region. This ensures active regulation of lubricant outflow. The integral reaction of the forces at element 3 and membrane 4 is balanced by the drag associated with elastic deformation of membrane 4 . The continuity of the gas flow through the pressure line, which ensures active pressure redistribution, leads to smaller eccentricity e of the shaft and the bearing housing and hence to smaller pliability ∂ e / ∂ f . The bearing pliability will decrease with increase in radial pliability of the membrane and hence greater eccentricity of the annular elements 3 and the bearing housing. In investigating the static characteristics, we assume that the axes of the housing and the mobile elements are parallel. Dimensionless variables are employed in the calculations. Linear dimensions are referred to the shaft radius r 0 ; pressures to p in ; forces to π p in ; mass flow rates of the gas to / µ RT ; and gaps and eccentricities of the mobile elements to h 0 . Here h 0 is the thickness h of the supporting gas layer when the elements are coaxial (with no load f ); µ is the lubricant viscosity; R , T are, respectively, the universal gas constant and the absolute temperature of the lubricant. We consider the r0
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