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Application of disk springs as vibration isolators with quasi-zero stiffness is described. Analytical studies are made to determine the design parameters of the described vibration isolators. The model of a disk spring as a combination of a separate disk spring and an annular section is proposed.The operational reliability, longevity, and effi ciency of pumping and gas pumping units depend on a combination of factors. Vibration produces the most adverse effect -the share of trunk-line centrifugal pump failures due to elevated vibration level constitutes 38-45% [1, 2]. Also, in more than 90% cases sudden elevation of vibration level precedes failure of the units.The most promising and interesting solution of this problem is application of vibration-protection systems with quasi-zero stiffness, which allows creation of vibration isolator/insulator with low stiffness and signifi cant bearing capacity.We propose using as a vibration-isolating element disk springs which are distinguished by high permissible load with negligible deformation of the spring, compactness, simplicity of design and assembly, etc. Currently, disk springs are known in the shape of truncated cone (Fig. 1), which are made by stamping of sheet steel.State Standard GOST 3057-79 includes disk springs with diameters D = 28-300 mm, thickness s = 1-20 mm, and overall cone height h 0 = 0.6-9.0 mm. The maximum working compressive load for steel disk springs is 52·10 4 H [3]. Disk springs are generally made from 60S2A sheet steel (GOST 14959-69) or other steels similar in mechanical properties.Calculation of disk springs in strict formulation of the task was developed by Feodos'ev [4]. However, for applicable spring designs with diameter ratio D/d ≤ 3, use can be made of an approximate calculation method, according to which the dependence between the load P operating on the disk spring and its camber λ 1 is determined by the formula [3] P = 8πEs

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